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CN1807895B - Multistage compression type rotary compressor - Google Patents

Multistage compression type rotary compressor Download PDF

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Publication number
CN1807895B
CN1807895B CN 200610006023 CN200610006023A CN1807895B CN 1807895 B CN1807895 B CN 1807895B CN 200610006023 CN200610006023 CN 200610006023 CN 200610006023 A CN200610006023 A CN 200610006023A CN 1807895 B CN1807895 B CN 1807895B
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China
Prior art keywords
compression unit
pressure
cylinder
revolution
mentioned
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Expired - Fee Related
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CN 200610006023
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Chinese (zh)
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CN1807895A (en
Inventor
松本兼三
山崎晴久
只野昌也
里和哉
松浦大
斋藤隆泰
津田德行
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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Publication date
Priority claimed from JP2001366210A external-priority patent/JP2003166489A/en
Priority claimed from JP2001374296A external-priority patent/JP3762693B2/en
Priority claimed from JP2002015350A external-priority patent/JP2003214366A/en
Priority claimed from JP2002021338A external-priority patent/JP3762708B2/en
Priority claimed from JP2002028857A external-priority patent/JP2003227665A/en
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of CN1807895A publication Critical patent/CN1807895A/en
Application granted granted Critical
Publication of CN1807895B publication Critical patent/CN1807895B/en
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention provides a rotary compressor used to structurally simplify a laminae which divides a cylinder into a low-pressure chamber and a high-pressure chamber. In addition, the invention providesa multi-stage rotary compressor, the manufacturing method thereof and a defrosting device used in a coolant loop. The rotary compressor(10)comprises a first and a second rotary compressing units(32,34) which are driven via an electromotor(14) arranged in a sealed container(12). The first rotary compressing unit(32)is composed of an upper cylinder(38), a swinging piston(110) for a roller(112)whichis connected with an eccentric unit(42)on the rotary shaft(16)of the electromotor(14) and eccentrically moves inside the upper cylinder(38), and a laminae(114) which is molded on the swinging piston(110) and protrudes in the radial direction from the roller(112)to divide the upper cylinder(38)into a low-pressure chamber and a high-pressure chamber. A retaining member is arranged to retain the laminae(114) of the swinging piston(110)in a sliding and swingy mode.

Description

Multi-stage compression formula rotary compressor
The application is that the denomination of invention of on August 28th, 2002 application is dividing an application of 02142300.8 patent application for " rotary compressor, its manufacture method, and use the case apparatus that removes of this compressor ", application number.
Technical field
The invention still further relates to a kind of will being attracted to the second revolution compression unit and it is compressed the multi-stage compression formula rotary compressor that discharge the back by the refrigerant gas that discharge the first revolution compression unit compression back.
Background technology
The rotary compressor of existing for example bosom pressure-type multi-stage compression formula is drawn into gas (refrigerant gas) from the inlet hole of the first revolution compression unit low-pressure chamber side of cylinder, action compresses by cylinder and blade, become intermediate pressure, from the hyperbaric chamber side of cylinder through tap, discharge anechoic room and be discharged in the closed container.The gas of the intermediate pressure in this closed container is drawn into the low-pressure chamber side of cylinder by the inlet hole from the second revolution compression unit, carry out second level compression by the action of cylinder and blade, become the gas of HTHP, discharge through tap and discharge anechoic room from the hyperbaric chamber side.
The gas of discharging from rotary compressor flow into the radiator of refrigerant loop, after the heat radiation, by after the expansion valve throttling by the evaporimeter heat absorption, be drawn into the first revolution compression unit after the evaporation once more, and carry out this circulation repeatedly.
In addition, in this rotary compressor, when will be as the carbon dioxide (CO of the big cold-producing medium of height pressure reduction 2) as the occasion of cold-producing medium, discharging refrigerant pressure reaches 12MPa at the second revolution compression unit that becomes high pressure, on the other hand, become 8MPa (intermediate pressure) (suction pressure of the first revolution compression unit is 4MPa) at the first revolution compression unit that becomes rudimentary side.
In existing this multi-stage compression formula rotary compressor, particularly in bosom pressure multi-stage compression formula rotary compressor, refrigerant gas is drawn into the low-pressure chamber side of cylinder from the inlet hole of the first revolution compression unit, become intermediate pressure by the action compresses of cylinder and blade, pass through tap and discharge anechoic room being discharged in the closed container from the hyperbaric chamber side of cylinder.The cold-producing medium of the intermediate pressure in this closed container is drawn into the low-pressure chamber side of cylinder from the inlet hole of the second revolution compression unit, carry out second level compression by the action of cylinder and blade, become the refrigerant gas of HTHP, flow into outside radiator through tap, discharge anechoic room from the hyperbaric chamber side.
In addition,, dump valve is set at the first and second discharge anechoic rooms that turn round compression units in order to prevent from cylinder, to be discharged to after the compression refluence of the cold-producing medium of discharging anechoic room, but by this inaccessible tap in dump valve freely openable ground.
Use the big cold-producing medium of height pressure reduction for example carbon dioxide as the occasion of cold-producing medium, discharging refrigerant pressure becomes 12MPa at the second revolution compression unit that becomes high pressure HP as shown in Figure 8, on the other hand, become 8MPa (intermediate pressure MP) (the suction pressure LP of the first revolution compression unit is 4MPa) at the first revolution compression unit that becomes rudimentary side.As a result, partial level differential pressure (the discharge pressure HP's of the suction pressure MP of the second revolution compression unit and the second revolution compression unit is poor) is up to 4MPa.In addition, when outside air temperature low and when making the evaporating temperature step-down of cold-producing medium, the discharge pressure MP step-down of the revolution compression unit of the first revolution compression unit, so partial level differential pressure (the discharge pressure HP of the suction pressure MP of the second revolution compression unit and the second revolution compression unit) further increases.
In existing this multi-stage compression formula rotary compressor, particularly in bosom pressure-type multi-stage compression formula rotary compressor, refrigerant gas is drawn into the low-pressure chamber side of cylinder from the inlet hole of the first revolution compression unit, become intermediate pressure by the action compresses of cylinder and blade, being discharged in the closed container through tap and discharge anechoic room from the hyperbaric chamber side of cylinder. the cold-producing medium of the intermediate pressure in this closed container is drawn into the low-pressure chamber side of cylinder from the inlet hole of the second revolution compression unit, carry out second level compression by the action of cylinder and blade, become the refrigerant gas of HTHP, from hyperbaric chamber side process tap, discharge anechoic room and flow into radiator, after the heat radiation, by the expansion valve throttling, in evaporimeter, absorb heat, be drawn into the first revolution compression unit, and carry out this circulation repeatedly.
In existing this refrigerant loop, particularly in the refrigerant loop that uses bosom pressure-type multi-stage compression formula rotary compressor, refrigerant gas is drawn into the low-pressure chamber side of cylinder from first inlet hole that turns round compression unit of multi-stage compression formula rotary compressor, become intermediate pressure by the action compresses of cylinder and blade, pass through tap and discharge anechoic room being discharged in the closed container from the hyperbaric chamber side of cylinder.Refrigerant gas in this closed container is drawn into the low-pressure chamber side of cylinder from the inlet hole of the second revolution compression unit, carry out second level compression by the action of cylinder and blade, become the refrigerant gas of HTHP, flow into the radiators such as gas cooler that constitute refrigerant loop from the hyperbaric chamber side through tap, discharge anechoic room, given play to thermolysis by heat radiation, afterwards, by expansion valve (decompressor) throttling, flow into evaporimeter, absorb heat there and evaporate, afterwards, be drawn into the first revolution compression unit, and carry out this circulation repeatedly.
In addition, in this multi-stage compression formula rotary compressor, when inciting somebody to action for example CO of the big cold-producing medium of height pressure reduction 2(carbon dioxide) as the occasion of cold-producing medium, discharging refrigerant pressure reaches 12MPa at the second revolution compression unit that becomes high pressure, on the other hand, becomes 8MPa at the first revolution compression unit that becomes rudimentary side, and it becomes the intermediate pressure in the closed container.The suction pressure of the first revolution compression unit is about 4MPa.
Here, the blade that is used by rotary compressor is inserted in the gathering sill radially of being located at cylinder with can move freely.This blade need be pressed to the cylinder side often, so, except as in the past, blade being pressed to the cylinder side, also in cylinder, form back pressure chamber by spring, add at this back pressure chamber to be used for blade is applied the back pressure of power towards the cylinder side, cause complex structureization.
Particularly in the second revolution compression unit of as described above bosom pressure-type multi-stage compression formula rotary compressor, because the intermediate pressure height in the pressure ratio closed container in the cylinder, so existence need apply the problem of passage of the back pressure of high pressure at back pressure chamber.
To for example carbon dioxide (CO of the big cold-producing medium of height pressure reduction 2) as the occasion of cold-producing medium, discharging refrigerant pressure reaches more than the 12MPa at the second revolution compression unit that becomes high pressure HP as shown in Figure 9, on the other hand, when externally temperature is 15 ℃ 8MPa (intermediate pressure) (the suction pressure LP of the first revolution compression unit is 4MPa) at the first revolution compression unit that becomes rudimentary side.As a result, the level differential pressure of the first order (the discharge pressure MP's of the suction pressure LP of the first revolution compression unit and the first revolution compression unit is poor) is up to 4MPa.In addition, because the high more then discharge pressure MP of the first revolution compression unit of outside air temperature becomes high more sharp, so the level differential pressure of the first order (the discharge pressure MP's of the suction pressure LP of the first revolution compression unit and the first revolution compression unit is poor) becomes bigger.
When the level differential pressure of the first order increases like this, the inside and outside pressure differential of the dump valve that opens and closes of tap of the first revolution compression unit is become excessive, there is the problem of durability such as dump valve breakage and reliability decrease.
When partial level differential pressure increased like this, the inside and outside pressure differential of dump valve of the second revolution compression unit became excessive, had the problem of the dump valve breakage of this pressure official post second revolution compression unit.
The blade that is installed on such multi-stage compression formula rotary compressor is inserted in the radial slot of being located at cylinder with can move freely.This blade is pushed to cylinder and will be divided into low-pressure chamber side and hyperbaric chamber side in the cylinder, be provided with towards the cylinder side at the rear side of blade this blade is applied the spring of elastic force, and the back pressure chamber that is communicated with the hyperbaric chamber of cylinder is set in groove for blade being applied power towards the cylinder side.
In the rotary compressor of bosom pressure-type, because the pressure height in the pressure ratio closed container in the cylinder of the second revolution compression unit, so the back pressure chamber that applies power at the blade to this second revolution compression unit applies the pressure that second cold-producing medium that turns round compression unit is discharged side.
Yet, when in this multi-stage compression formula rotary compressor, using for example carbon dioxide (CO of the big cold-producing medium of difference of height 2) as the occasion of cold-producing medium, as shown in Figure 8, discharging refrigerant pressure reaches 12MPa at the second revolution compression unit that becomes high pressure (HP).For this reason, be added to the occasion of back pressure chamber at the pressure of the cold-producing medium of the second revolution compression unit being discharged side, the pressure that blade is pressed to cylinder exceeds the value of needs, sliding part in blade front end and cylinder periphery increases burden significantly, blade and cylinder noticeable wear produce damaged such problem under the worst situation.
Particularly use for example carbon dioxide (CO of the big cold-producing medium of difference of height at this multi-stage compression formula rotary compressor 2) as the occasion of cold-producing medium, as shown in Figure 7, discharging refrigerant pressure reaches 12MPa at the second revolution compression unit that becomes high pressure (HP), becomes 8MPa (intermediate pressure MP) (the suction pressure LP of the first revolution compression unit is 4MPa) at the first revolution compression unit that becomes rudimentary side.As a result, partial level differential pressure (the discharge pressure HP's of the suction pressure MP of the second revolution compression unit and the second revolution compression unit is poor) is up to 4MPa.Particularly low outside air temperature makes the discharge pressure MP step-down of the first revolution compression unit, so, partial level differential pressure (the discharge pressure HP's of the suction pressure MP of the second revolution compression unit and the second revolution compression unit is poor) becomes bigger, the compression load of the second revolution compression unit increases, and has the problem of durability and reliability decrease.
Therefore in the past, make the eliminating volume of the eliminating volumetric ratio first revolution compression unit of the second revolution compression unit change thickness (highly) size of the cylinder of the first revolution compression unit littlely, get rid of volumetric ratio with diminishing thereby partial level differential pressure is set.
Yet in such establishing method, because thickness (highly) size of first cylinder becomes big, the cylinder material of the necessary for this reason change first revolution compression unit, eccentric part, cylinder etc. are parts all.In addition, the thickness of cylinder (highly) size becomes makes thickness (highly) size of rotary compressor structure portion also become greatly greatly, so the overall dimensions of multi-stage compression formula rotary compressor also becomes greatly, and the problem that exists the miniaturization of compressor to be difficult to realize.
In the refrigerant loop that uses such multi-stage compression formula rotary compressor, because evaporimeter frosting, so must defrost, but when make for the defrosting of carrying out this evaporimeter the high temperature refrigerant of discharging from the second revolution compression unit can't help decompressor decompression ground supply to evaporimeter (though comprise the occasion that directly supplies to evaporimeter and by decompressor but there decompression ground by the occasion of ground supply) time, the suction pressure of the first revolution compression unit rises, like this, the discharge pressure (intermediate pressure) of the first revolution compression unit uprises.This cold-producing medium is discharged by the second revolution compression unit, but owing to do not reduce pressure, so it is identical with the suction pressure of the first revolution compression unit that the discharge pressure of the second revolution compression unit becomes, so, exist by second and turn round the discharge of compression unit and the problem that suction produces the reverse phenomenon of pressure.
Here, to supply to the refrigerant loop of evaporimeter from the cold-producing medium that the first revolution compression unit is discharged with being provided for not reducing pressure, as will also supplying with evaporimeter from the cold-producing medium that the first revolution compression unit is discharged, then can avoid the discharge of the second revolution compression unit and the pressure of suction to reverse during defrosting by this refrigerant loop.
Yet, in this occasion, the discharge side of the discharge side of the first revolution compression unit and the second revolution compression unit is communicated with, making the suction side of the second revolution compression unit thus and discharging side is uniform pressure, so, the takeoff problem of fluctuation of service of grade in an imperial examination two-revolution compression unit of the blade that exist to produce the second revolution compression unit.
Summary of the invention
The present invention makes for the problem that solves the prior art, and its purpose is to provide a kind of rotary compressor, and this rotary compressor can be simplified and will be divided into the structure of the blade of low-pressure chamber side and hyperbaric chamber side in the cylinder.
The present invention makes for the problem that solves the prior art, and its purpose is to provide a kind of multi-stage compression formula rotary compressor, excessive durability that causes of level differential pressure and reliability decrease that this multi-stage compression formula rotary compressor can be avoided the first order in advance.
The present invention makes for the problem that solves the prior art, its purpose is to provide a kind of multi-stage compression formula rotary compressor, and this multi-stage compression formula rotary compressor can be avoided the breakage failure of the dump valve of the second revolution compression unit that partial level differential pressure causes etc. in advance.
The present invention makes for the problem that solves the prior art, its purpose is to provide a kind of bosom pressure-type multi-stage compression formula rotary compressor, this bosom pressure-type multi-stage compression formula rotary compressor can improve the durability of blade and cylinder, avoids the breakage of blade and cylinder in advance.
In addition, the present invention makes for the problem that solves the prior art, its purpose is to provide a kind of manufacture method of multi-stage compression formula rotary compressor, the manufacture method of this multi-stage compression formula rotary compressor can do one's utmost to reduce the change of parts, reduce cost, and, can prevent that the size of compressor from enlarging, can easily set the best volumetric ratio of getting rid of simultaneously.
In addition, the present invention makes for the problem that solves the prior art, its purpose is to provide a kind of defroster, the irregular operation situation that this defroster produces in the time of can avoiding the Defrost operation of evaporimeter in the refrigerant loop that has utilized multi-stage compression formula rotary compressor.
According to multi-stage compression formula rotary compressor of the present invention, the first and second revolution compression units that in closed container, have electrodynamic element and drive by this electrodynamic element, to be attracted to the above-mentioned second revolution compression unit by above-mentioned first revolution compression unit compression and the refrigerant gas of discharging, and compress the back and discharge; It is characterized in that: be provided with the cold-producing medium suction side and cold-producing medium access of discharging side and the valve gear that opens and closes this access that are communicated with the above-mentioned first revolution compression unit, the pressure differential that this valve gear is discharged side at the above-mentioned first revolution cold-producing medium suction side of compression unit and cold-producing medium reaches the set upper limit value when above, open above-mentioned access.
In a first aspect of the present invention, rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container revolution compression unit is to CO 2Cold-producing medium compresses; Wherein, comprise the cylinder that is used to constitute the revolution compression unit, has the oscillating-piston that engages with the eccentric part of the gyroaxis that is formed at electrodynamic element and in cylinder, carry out the eccentric cylinder portion that moves, be formed at this oscillating-piston and will be divided into the blade part of low-pressure chamber side and hyperbaric chamber side in the cylinder towards radially protruding from cylinder portion, and be located at cylinder and can be free to slide and swingingly keep the maintaining part of the blade part of oscillating-piston, so, corresponding with the off-centre revolution of the eccentric part of gyroaxis, oscillating-piston is the center swing with the maintaining part and slides that its blade part will be divided into low-pressure chamber side and hyperbaric chamber side often in the cylinder.
Like this, there is no need as the past, to be provided with towards the cylinder side blade is applied the spring of power and back pressure chamber and applies the structure of back pressure at this back pressure chamber, can realize the simplification of structure of rotary compressor and the reduction of production cost.
In a second aspect of the present invention, rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units will be by the CO of the first revolution compression unit compression 2Refrigerant gas is discharged in the closed container, in addition, is compressed the gas of the intermediate pressure of this discharge by the second revolution compression unit; Wherein, comprise the cylinder that constitutes the second revolution compression unit, has the oscillating-piston that engages with the eccentric part of the gyroaxis that is formed at electrodynamic element and in cylinder, carry out the eccentric cylinder portion that moves, be formed at this oscillating-piston and will be divided into the blade part of low-pressure chamber side and hyperbaric chamber side in the cylinder towards radially protruding from cylinder portion, and be located at cylinder and can be free to slide and swingingly keep the maintaining part of the blade part of oscillating-piston, so, similarly corresponding with the off-centre revolution of the eccentric part of gyroaxis, oscillating-piston is the center swing with the maintaining part and slides that its blade part is divided into low-pressure chamber side and hyperbaric chamber side in the cylinder with the second revolution compression unit often.
Like this, do not need to be provided with as the past towards the cylinder side and blade is applied the spring and the back pressure chamber of power and this back pressure chamber is applied the structure of back pressure.Particularly in closed container as the present invention, become in the so-called multi-stage compression formula rotary compressor of intermediate pressure, apply the complex structureization of back pressure, but by using oscillating-piston, significantly simplified construction and reducing production costs.
A third aspect of the present invention first or the basis of second aspect on, constitute maintaining part by gathering sill and sleeve, the blade part that this gathering sill is formed at cylinder and oscillating-piston enters wherein with can move freely, this sleeve can be located at this gathering sill freely to rotate and can keep blade part with being free to slide, so, can realize the swing of oscillating-piston and the tranquilization of sliding action.Like this, can increase substantially the Performance And Reliability of rotary compressor.
According to the present invention, multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, to be attracted to the above-mentioned second revolution compression unit by the first revolution compression unit compression and the refrigerant gas of discharging, and compress the back and discharge; Wherein, be provided with the cold-producing medium suction side and cold-producing medium access of discharging side and the valve gear that opens and closes this access that are communicated with the first revolution compression unit, the pressure differential that this valve gear is discharged side at the first revolution cold-producing medium suction side of compression unit and cold-producing medium reaches the set upper limit value when above, the open communication road, so, the pressure differential of discharging side as the cold-producing medium suction side level differential pressure, the first revolution compression unit and the cold-producing medium of the first order can be suppressed to below the set upper limit value.Like this, the level differential pressure that can in advance avoid the first order is excessive and cause being located at the problems such as dump valve breakage of the first revolution compression unit, can improve the durability and the reliability of rotary compressor.
According to a fifth aspect of the present invention, has the cylinder that constitutes the first revolution compression unit, the opening surface of inaccessible this cylinder also has the supporting member of bearing of the gyroaxis of electrodynamic element, be formed in the suction passage in this supporting member and discharge anechoic room, in supporting member, form access, suction passage and discharge anechoic room are communicated with, simultaneously, valve gear is located in the supporting member, so, can access and valve gear is intensive in the cylinder of the first revolution compression unit and realize miniaturization, simultaneously, because assembled valve device in cylinder in advance is so assembling operation also improves.
Promptly, in the present invention, the first and second revolution compression units that have electrodynamic element and driven by this electrodynamic element in closed container will be attracted to the second revolution compression unit, the discharge of compression back by first refrigerant gas that turns round the intermediate pressure of compression unit compression; Wherein, be provided with connection and discharge the access of side and the valve gear that this access is opened and closed by the cold-producing medium that passes through the path and the second revolution compression unit of the refrigerant gas of the intermediate pressure of the first revolution compression unit compression, the pressure differential that this valve gear is discharged the refrigerant gas of side at the cold-producing medium of the refrigerant gas of intermediate pressure and the second revolution compression unit reaches the occasion more than the set upper limit value, the open communication road, so, can be that second level differential pressure suppresses lowlyer than set upper limit value with the pressure differential of discharge pressure and the suction pressure of the second revolution compression unit.
Like this, can avoid the faults such as breakage of the dump valve of the second revolution compression unit to take place in advance.
A seventh aspect of the present invention is on the basis of foregoing, have cylinder that constitutes the second revolution compression unit and the discharge anechoic room of discharging refrigerant compressed gas in this cylinder, to be discharged in the closed container by first refrigerant gas that turns round the intermediate pressure of compression unit compression, the second revolution compression unit attracts the refrigerant gas of the intermediate pressure in this closed container, simultaneously, access is formed on and surrounds in the wall of discharging anechoic room, be communicated with in the closed container and the discharge anechoic room, valve gear is located in the above-mentioned wall, so, can in the wall of the second revolution compression unit, intensive connection turn round the valve gear that the cold-producing medium of compression unit is discharged the access of side and opened and closed access by the path and second of passing through of the refrigerant gas of the intermediate pressure of the first revolution compression unit compression.
Like this, can realize the simplification of constructing and the miniaturization of overall dimensions.
According to the present invention, multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, to be discharged in the closed container by the first revolution compression unit refrigerant compressed gas, in addition, compress the refrigerant gas of the intermediate pressure of this discharge by the second revolution compression unit; Wherein, has the cylinder that is used to constitute the second revolution compression unit, join to be incorporated in the eccentric part of the gyroaxis that is formed at electrodynamic element and carry out eccentric rotating cylinder in the cylinder, be contacted with this cylinder and will be divided into the blade of low-pressure chamber side and hyperbaric chamber side in the cylinder, be used for towards the cylinder side this blade being applied often the back pressure chamber of power, the cold-producing medium that is communicated with the second revolution compression unit is discharged the access of side and back pressure chamber, be used to adjust the pressure-regulating valve that is added to the pressure of back pressure chamber by this access, so, by this pressure-regulating valve, can suitably keep the pushing force of blade to cylinder. in addition, to discharge the pressure of side than the cold-producing medium of the second revolution compression unit low by as a ninth aspect of the present invention the pressure of back pressure chamber being remained, than the high setting of the pressure in the closed container, can prevent that so-called blade from takeofing, prevent to apply above the back pressure that needs, the power optimization that blade is applied cylinder at blade.
Like this, can alleviate the burden of the slipper that is applied to blade front end and cylinder periphery, avoid the breakage of blade and cylinder in advance, improve durability.
According to a tenth aspect of the present invention on the basis of foregoing, also be provided with inaccessible cylinder opening surface and have electric element gyroaxis bearing supporting member and be formed in discharge anechoic room in this supporting member, in supporting member, form access, be communicated with and discharge anechoic room and back pressure chamber, and pressure-regulating valve is arranged in the supporting member, so, can effectively utilize the limited space in the closed container, can't make complex structureization, the pressure in the back pressure chamber of adjustable blade.In addition, owing in advance access and pressure-regulating valve are set in supporting member, so assembling operation is also good.
The manufacture method of multi-stage compression formula rotary compressor of the present invention is made multi-stage compression formula rotary compressor, this multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, these first and second revolutions compression units are by first and second cylinders and engage with first and second eccentric parts of the gyroaxis that is formed at above-mentioned electrodynamic element and carry out rotating first and second cylinders of off-centre constitute in cylinder, simultaneously, the refrigerant gas of being discharged by the above-mentioned first revolution compression unit compression back attracted to the second revolution compression unit, discharge the compression back, when making this multi-stage compression formula rotary compressor, do not change thickness (highly) size of first cylinder, by changing the internal diameter of this cylinder, can set the eliminating volumetric ratio of the first and second revolution compression units.
For this reason, need not change all parts such as eccentric part of the first revolution cylinder material of compression unit and cylinder, gyroaxis, for example can do one's utmost to be suppressed to and only change cylinder or only change cylinder and eccentric part etc., can reduce cost.In addition, owing to can prevent the expansion of the overall dimensions of compressor, so, also can make compact in size.
In addition, be in the manufacture method of basic multi-stage compression formula rotary compressor with foregoing in a twelveth aspect of the present invention, with more than 40% below 75% of the eliminating volume of eliminating volume settings to the first revolution compression unit of the second revolution compression unit.
Like this, as with 40% or more below 75% of the eliminating volume of eliminating volume settings to the first revolution compression unit of the second revolution compression unit, then the eliminating volumetric ratios of the first and second revolution compression units are the best.
For defroster of the present invention, refrigerant loop by multi-stage compression formula rotary compressor, gas cooler, first decompressor, and evaporimeter constitute, this multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units turn round the compression unit compression by the cold-producing medium after the first revolution compression unit compression by second; This gas cooler flows into wherein the cold-producing medium of discharging from the second revolution compression unit of this multi-stage compression formula rotary compressor; This first decompressor is connected to the outlet side of this gas cooler; This evaporimeter is connected to the outlet side of this first decompressor; The cold-producing medium that comes out from this evaporimeter is compressed by the first revolution compression unit; Wherein, have and do not supply with from the defrost circuit of the cold-producing medium of the first and second revolution compression units discharges to evaporimeter with reducing pressure, control the first stream control device of the cold-producing medium circulation of this defrost circuit, be located at and be used for to supply to second decompressor of the refrigerant passage of the second revolution compression unit from the cold-producing medium of the first revolution compression unit discharge, make cold-producing medium flow to this second decompressor or make cold-producing medium walk around the second stream control device that this second decompressor ground is controlled with flowing through, when making cold-producing medium flow to defrost circuit by the first stream control device, this second stream control device makes cold-producing medium flow to second decompressor, so, during the evaporator defrost operation, the discharging refrigerant of the first revolution compression unit and the second revolution compression unit does not supply to evaporimeter with not reducing pressure, can avoid the pressure of the second revolution compression unit to reverse phenomenon thus.
Particularly according to the present invention, when defrosting, the cold-producing medium that supplies to the second revolution compression unit supplies to the second revolution compression unit by the decompressor of being located at coolant channel, so, the pressure differential of formation regulation between suction in the second revolution compression unit and the discharge.
Like this, second turns round the stable of compression unit, and reliability also improves.Particularly as a fourteenth aspect of the present invention, with CO 2In the refrigerant loop of gas as the cold-producing medium use, particularly can obtain obvious effects.
Description of drawings
Fig. 1 is the skiagraph of the rotary compressor of the embodiment of the invention.
Fig. 2 is the amplification profile diagram of oscillating-piston part of the second revolution compression unit of the rotary compressor of Fig. 1.
Fig. 3 is the skiagraph of the multi-stage compression formula rotary compressor of the embodiment of the invention.
Fig. 4 is the amplification profile diagram of access part of the first revolution compression unit of the multi-stage compression formula rotary compressor of Fig. 3.
Fig. 5 is the following figure of lower support member of the multi-stage compression formula rotary compressor of Fig. 3.
Fig. 6 is the upper support member of multi-stage compression formula rotary compressor of Fig. 3 and the top figure of upper cap.
Fig. 7 is the following figure of lower cylinder of the multi-stage compression formula rotary compressor of Fig. 3.
Fig. 8 is the top figure of upper cylinder of the multi-stage compression formula rotary compressor of Fig. 3.
Fig. 9 is the figure of relation that the pressure of the outside air temperature of two stage compression type rotary compressors and each several part is shown.
Figure 10 is the skiagraph of the multi-stage compression formula rotary compressor of the embodiment of the invention.
Figure 11 is the amplification profile diagram of access part of the second revolution compression unit of the multi-stage compression formula rotary compressor of Figure 10.
Figure 12 is the amplification profile diagram of access part of the second revolution compression unit of the multi-stage compression formula rotary compressor of another embodiment.
Figure 13 is the skiagraph of the multi-stage compression formula rotary compressor of the embodiment of the invention.
Figure 14 is the amplification profile diagram of pressure-regulating valve part of the second revolution compression unit of the multi-stage compression formula rotary compressor of Figure 13.
Figure 15 is the front elevation of the multi-stage compression formula rotary compressor of Figure 13.
Figure 16 is the side view of the multi-stage compression formula rotary compressor of Figure 13.
Figure 17 is the refrigerant loop figure of hot water supply apparatus that has utilized the multi-stage compression formula rotary compressor of Figure 13.
Figure 18 is the skiagraph of the multi-stage compression formula rotary compressor of the embodiment of the invention.
Figure 19 is the skiagraph that is adapted to the multi-stage compression formula rotary compressor of embodiments of the invention.
Figure 20 is the refrigerant loop figure that has used hot water supply apparatus of the present invention.
The specific embodiment
Below, describing form of implementation of the present invention with reference to the accompanying drawings in detail. Fig. 1 illustrates the skiagraph of bosom pressure-type multistage (secondary) compression type rotary compressor 10 with first and second revolution compression units 32,34 as the embodiment of rotary compressor of the present invention.
In the figure, symbol 10 is with carbon dioxide (CO 2) the bosom pressure-type multi-stage compression formula rotary compressor that uses as cold-producing medium, the closed container cylindraceous 12 that this rotary compressor 10 is made of steel plate, electrodynamic element 14, and rotary compressor structure portion 18 constitute, electrodynamic element 14 configuration is contained in this closed container 12 inner space upsides, and this rotary compressor structure portion 18 comprises and is disposed at these electrodynamic element 14 downsides and turns round compression unit 34 (second level) by the first revolution compression unit 32 (first order) and second that the gyroaxis 16 of electrodynamic element 14 drives.
It is little that the eliminating volume settings of the second revolution compression unit 34 of the rotary compressor 10 of embodiment must be got rid of volume than the first revolution compression unit 32.
Closed container 12 with the bottom as oil groove, bowl-shape end cap (lid) 12B that is substantially by the upper opening of the vessel 12A that accommodates electrodynamic element 14 and rotary compressor structure portion 18 and inaccessible this vessel 12A constitutes, and installation is used to feed electrical power to the terminal (having omitted distribution) 20 of electrodynamic element 14 on this end cap 12B.
Electrodynamic element 14 is mounted to the stator 22 of ring-type by the inner peripheral surface along closed container 12 upper spaces and in the inboard of this stator 22 rotor 24 that inserts configuration in plurality of gaps ground is set and constitutes.This rotor 24 is fixed on the gyroaxis 16 that extends along by the vertical direction at center.
Stator 22 have layered product 26 that the electromagnetic steel plate of the ring-type of laminating obtains and with string around (concentrate and reel) mode package in the stator coil 28 of the tooth portion of this layered product 26.In addition, rotor 24 is similarly formed by the layered product 30 of electromagnetic steel plate with stator 22, inserts permanent magnet MG in this layered product 30.
Clamping central dividing plate 36 between the above-mentioned first revolution compression unit 32 and the second revolution compression unit 34.This first revolution compression unit 32 and the second revolution compression unit 34 by central dividing plate 36, be disposed at this central dividing plate 36 up and down upper cylinder 38, lower cylinder 40, be positioned at this upper and lower air cylinders 38,40 and have 180 and be located at upper support member 54 and the lower support member 56 that the eccentric part up and down 42,44 of gyroaxis 16 and inaccessible upper cylinder 38 upside opening surfaces and lower cylinder 40 open lower side faces be also used as the bearing of gyroaxis 16 with spending phase differences and constitute as supporting member.
Be provided with at the first revolution compression unit 32 and engage with following eccentric part 44 and carry out eccentric rotating bottom roll 48 and be contacted with this bottom roll 48 and be divided into the blade 52 of low-pressure chamber side and hyperbaric chamber side in lower cylinder 40.Accommodate the gathering sill and the spring 76 that is disposed at this gathering sill outside of blade 52 at lower cylinder 40, this spring 76 is contacted with the outboard end of blade 52, towards cylinder 48 sides blade 52 is applied elastic force often with being provided for being free to slide.In the resettlement section of closed container 12 sides of this spring 76, metal latch 137 is set, spring 76 is played the effect of anticreep.
The gathering sill of lower cylinder 40 is distolateral being communicated in the closed container 12 in the outside of blade 52, and like this, the intermediate pressure described later in the closed container 12 constitutes as the back pressure of blade 52 with applying.
In addition, in the upper cylinder 38 of the second revolution compression unit 34 oscillating-piston 110 is set, this oscillating-piston 110 constitutes (Fig. 2) by cylinder portion 112 and blade part 114.Cylinder portion 112 is engaged in the last eccentric part 42 of gyroaxis 16, and last eccentric part 42 turns round in this cylinder portion 112, and it is mobile that the inner face that cylinder portion 112 self and the off-centre revolution of last eccentric part 42 are contacting to upper cylinder 38 accordingly carries out off-centre.
Towards radially outstanding, the maintenance groove 116A ground that enters into sleeve 116 described later is kept blade part 114, will be divided into low-pressure chamber side and hyperbaric chamber side ground formation (Fig. 2) in the upper cylinder 38 from this cylinder portion 112.
In addition, form the gathering sill 70 that radially extends from the interior Zhou Dynasty, expand the retaining hole 88 that open form becomes general cylindrical shape along the vertical direction at the medial extremity of this gathering sill 70 at upper cylinder 38.In this retaining hole 88, insert above-mentioned sleeve 116, this sleeve 116 retaining hole 88 in can with upper and lower to spool be that the center is kept freely to rotate.
Center by this sleeve 116 connects along radially (upper cylinder 38 radially) of this sleeve 116 and forms above-mentioned maintenance groove 116A, the blade part 114 of oscillating-piston 110 enters into gathering sill 70, keep in the groove 116A by this, can remain in this maintenance groove 116A. under this state with being free to slide, blade part 114 can move freely in gathering sill 70, simultaneously, sleeve 116 self revolution, thus oscillating-piston 110 also can be free to slide reposefully self and swingingly be kept.
Promptly, oscillating-piston 110 joins the last eccentric part 42 of the gyroaxis 16 that is formed at electrodynamic element 14 to, in upper cylinder 38, have the eccentric cylinder portion 112 that moves, be provided with from this cylinder portion 112 and will be divided into the blade part 114 of low-pressure chamber side and hyperbaric chamber side in this upper cylinder 38 towards radially outstanding.Oscillating-piston 110 swing in upper cylinder 38 along with the off-centre revolution of last eccentric part 42.Constitute maintaining part of the present invention in this occasion by this gathering sill 70 and sleeve 116.
In this occasion, 116 in retaining hole 88 and sleeve and keep groove 116A and 114 of blade parts can not flow out second turn round compression unit 34 discharge pressure form the size that seals by oil.By forming such structure, do not need the blade 52 of being located at the first revolution compression unit 32 to be applied the spring of elastic force at the second revolution compression unit 34 towards cylinder 48 sides.In addition, in the occasion that as the first revolution compression unit 32, constitutes the second revolution compression unit 34, though add back pressure at blade, towards the cylinder side blade is applied power, but owing to be provided with oscillating-piston 110 at the second revolution compression unit 34, so, do not need back pressure towards blade.By can being free to slide by sleeve 116 and swingingly keeping oscillating-piston 110, thereby the tranquilization of the action of the blade part 114 that produces by oscillating-piston 110 can be realized, the performance of rotary compressor 10 can be increased substantially.
On the other hand, form the discharge anechoic room 62,64 that caves in upper support member 54 and lower support member 56, simultaneously, the peristome of these two discharge anechoic rooms 62,64 is inaccessible by lid respectively.That is, discharge anechoic room 62, discharge anechoic room 64 by lower cover 68 obturations as lid by upper cap 66 obturations as lid.
Electrodynamic element 14 sides of the upper cap 66 in discharging anechoic room 64 and closed container 12 are communicated with by connecting upper and lower air cylinders 38,40 and the central dividing plate 36 ground access towards closed container 12 inner openings.
In this occasion, as cold-producing medium, use and do not destroy earth environment, consider the above-mentioned carbon dioxide (CO as the nature cold-producing medium such as combustibility and toxicity 2), for example use existing oil such as mineral oil, alkylbenzene oil, ether oil, ester oil as the oil of lubricating oil.
The side of the vessel 12A of closed container 12 with upper support member 54, lower support member 56, discharge anechoic room 62, and the corresponding position of the upside (position corresponding substantially) of upper cap 66 with the lower end of electrodynamic element 14 weld fixed sleeving 141,142,143 respectively, reach 144.Sleeve pipe 141 and sleeve pipe adjacency about in the of 142, simultaneously, sleeve pipe 143 is positioned on the big body diagonal of sleeve pipe 141.In addition, sleeve pipe 144 is positioned at the position of staggering 90 degree substantially with sleeve pipe 141.
Insert the end that connection is used for refrigerant gas is directed into the cold-producing medium ingress pipe 92 of upper cylinder 38 in sleeve pipe 141, an end of this cold-producing medium ingress pipe 92 is communicated to the suction passage of upper cylinder 38.This cold-producing medium ingress pipe 92 arrives sleeve pipe 144 by the upside of closed container 12, and the other end inserts and is connected in the sleeve pipe 144, thereby is communicated in the closed container 12.
In addition, insertion connects an end that refrigerant gas is directed into the cold-producing medium ingress pipe 94 of lower cylinder 40 in sleeve pipe 142, and an end of this cold-producing medium ingress pipe 94 is communicated to the suction passage of lower cylinder 40.The other end of this cold-producing medium ingress pipe 94 is connected to the lower end of not shown reservoir.In addition, insert connection refrigerant discharge leader 96 in sleeve pipe 143, an end of this refrigerant discharge leader 96 is communicated to discharges anechoic room 62.Symbol 147 is for being used to keep the carriage of above-mentioned reservoir.
Below with above formation explanation action.When by terminal 20 and not shown distribution during to stator coil 28 energisings of electrodynamic element 14, electrodynamic element 14 startings make rotor 24 revolutions.It is mobile by this revolution the cylinder portion 112 of the oscillating-piston 110 that joins the last eccentric part 42 that is provided with integratedly with gyroaxis 16 to be revolved round the sun as described above in upper cylinder 38, and the cylinder 48 that joins down eccentric part 44 to carries out the off-centre revolution in lower cylinder 40.
Like this, the refrigerant gas of low pressure (first order suction pressure LP:4MPa) that is drawn into the low-pressure chamber side of lower cylinder 40 via cold-producing medium ingress pipe 94 and the suction passage that is formed at lower support member 56 from not shown inlet hole is by the action compresses of cylinder 48 and blade 52, become intermediate pressure (MP1:8MPa), be discharged in the closed container 12 through above-mentioned access from the not shown tap of the hyperbaric chamber side of lower cylinder 40, the discharge anechoic room 64 that is formed at lower support member 56. making thus becomes intermediate pressure (MP1) in the closed container 12.
The refrigerant gas of the intermediate pressure in the closed container 12 comes out from sleeve pipe 144, is drawn into the low-pressure chamber side of upper cylinder 38 from not shown inlet hole via cold-producing medium ingress pipe 92 and the suction passage that is formed at upper support member 54.The refrigerant gas of the intermediate pressure that sucks carries out second level compression by the swing that can remain in the oscillating-piston 110 (blade part 114 and cylinder portion 112) that keeps groove 116A (this maintenance groove 116A is arranged on the sleeve 116 of the retaining hole 88 that can remain in upper cylinder 38 freely to rotate) with being free to slide, become the refrigerant gas (second level discharge pressure HP:12MPa) of HTHP, be discharged to the outside by not shown tap via the discharge anechoic room 62 that is formed at upper support member 54, refrigerant discharge leader 96 from the hyperbaric chamber side.The cold-producing medium of discharging flow into gas cooler etc.The refrigerant temperature of this moment is raised to substantially+and 100 ℃, the refrigerant gas of this HTHP dispels the heat, and for example the water in the hot water storage tank is heated, and produces substantially+90 ℃ hot water.
On the other hand, cold-producing medium is come out from gas cooler from cooling off in gas cooler.After not shown expansion valve decompression, also flow into not shown evaporimeter and produce evaporation, be drawn in the first revolution compression unit 32 from cold-producing medium ingress pipe 94 through above-mentioned reservoir, and carry out this circulation repeatedly.
Like this, have the upper cylinder 38 and the oscillating-piston 110 that are used to constitute the second revolution compression unit 34, this oscillating-piston 110 joins the last eccentric part 42 of the gyroaxis 16 that is formed at electrodynamic element 14 to and has the eccentric cylinder portion 112 that moves in upper cylinder 38, oscillating-piston 110 form from cylinder portion 112 towards radially outstanding and with upper cylinder 38 in be divided into the blade part 114 of low-pressure chamber side and hyperbaric chamber side, simultaneously, can be free to slide and swingingly keep the blade part 114 of oscillating-piston 110 at upper cylinder 38, so, do not need in the past such add the structure of back pressure and blade is applied the spring of elastic force towards the cylinder side at blade.Particularly in the such bosom pressure-type multi-stage compression formula rotary compressor of embodiment, do not need the discharge pressure of the second revolution compression unit 34 is applied to as back pressure the structure of blade, so, can simplify the structure of rotary compressor 10, reduce production costs significantly.
In the above-described embodiments, be not limited at the second revolution compression unit 34 oscillating-piston 110 is set, the occasion the present invention who oscillating-piston 110 is located at the first revolution compression unit 32 is also effective.But,, can reduce component costs by as embodiment, only the second revolution compression unit 34 being provided with oscillating-piston 110.In addition, in an embodiment, the present invention is adapted to the multi-stage compression formula rotary compressor of bosom pressure-type, but is not limited thereto, also effective for the cylinder of common single cylinder type.
Fig. 3 has the skiagraph of bosom pressure-type multistage (secondary) compression type rotary compressor 10 of the first and second revolution compression units 32,34 for the embodiment as multi-stage compression formula rotary compressor of the present invention illustrates.
In this Fig. 3, symbol 10 is with the bosom pressure-type multi-stage compression formula rotary compressor of carbon dioxide as cold-producing medium, the closed container cylindraceous 12 that this multi-stage compression formula rotary compressor 10 is made of steel plate, electrodynamic element 14, and rotary compressor structure portion 18 constitute, 14 configurations of this electrodynamic element are contained in this closed container 12 inner space upsides, and this rotary compressor structure portion 18 comprises that the first revolution compression unit 32 (first order) and second that the gyroaxis 16 by electrodynamic element 14 that is disposed at these electrodynamic element 14 downsides drives turns round compression unit 34 (second level).
Closed container 12 with the bottom as oil groove, bowl-shape end cap (lid) 12B that is substantially by the upper opening of the vessel 12A that accommodates electrodynamic element 14 and rotary compressor structure portion 18 and inaccessible this vessel 12A constitutes, and, be formed centrally circular installing hole 12D on this end cap 12B, the terminal (having omitted distribution) 20. that is used to feed electrical power to electrodynamic element 14 is installed at this installing hole 12D
Electrodynamic element 14 is mounted to the stator 22 of ring-type and in the inboard of this stator 22 some rotors that insert configuration with gap 24 is set by the inner peripheral surface along closed container 12 upper spaces and constitutes.This rotor 24 is fixed on the gyroaxis 16 that extends along by the vertical direction at center.
Stator 22 have layered product 26 that the electromagnetic steel plate of the ring-type of laminating obtains and with string around (concentrate and reel) mode package in the stator coil 28 of the tooth portion of this layered product 26.In addition, rotor 24 is also similarly formed by the layered product 30 of electromagnetic steel plate with stator 22, inserts permanent magnet MG in this layered product 30.
Clamping central dividing plate 36 between the above-mentioned first revolution compression unit 32 and the second revolution compression unit 34.That is, the first revolution compression unit 32 and the second revolution compression unit 34 are by central dividing plate 36, be disposed at the cylinder 38 up and down of this central dividing plate 36, cylinder 40, be positioned at this upper and lower air cylinders 38, in 40 and with the eccentric part up and down 42 of being located at gyroaxis 16 with having 180 degree phase differences, 44 cooperate and carry out eccentric rotating up-down roller 46,48, be contacted with this up-down roller 46,48 with upper and lower air cylinders 38, be divided into the blade up and down 50 of low-pressure chamber side and hyperbaric chamber side in 40 respectively, 52, reach upper support member 54 and lower support member 56 formations that inaccessible upper cylinder 38 upside opening surfaces and lower cylinder 40 open lower side faces are also used as the bearing of gyroaxis 16 as supporting member.
Form by inlet hole 161,162 at upper support member 54 and lower support member 56 and to be communicated to the suction passage 58,60 of inside of upper and lower air cylinders 38,40 and the discharge anechoic room 62,64 of depression respectively, and the peristome of these two discharge anechoic rooms 62,64 is inaccessible by lid respectively.That is, discharge anechoic room 62, discharge lid 68 obturations of anechoic room 64 by the bottom of conduct lid by lid 66 obturations as the top of covering.
In this occasion, erect in the central authorities of upper support member 54 and to form bearing 54A.In addition, at the perforation formation bearing 56A of central authorities of lower support member 56, gyroaxis 16 remains in the bearing 54A of upper support member 54 and the bearing 56A of lower support member 56.
Formation access 100 in the suction passage 60 of the above-mentioned first revolution compression unit 32 and the lower support member 56 of discharging between the anechoic room 64.This access 100 is discharged the passage of the discharge anechoic room 64 of side for the suction passage 60 of the cold-producing medium suction side that is communicated with the first revolution compression unit 32 and the cold-producing medium of the cold-producing medium of discharging the intermediate pressure that is obtained by the first revolution compression unit, 32 compression backs, and detailed content as shown in Figure 4.That is, make an end opening of first passage 101 discharging anechoic room 64, the other end of this first passage 101 is communicated with and discharges anechoic room 64 and valve gear reception room 102 at valve gear reception room 102 openings.
This valve gear reception room 102 vertically forms, and the lower openings of the upper opening of suction passage 60 sides and lower cover 68 sides is respectively by seal 104,105 obturations.
Make an end opening of second channel 103 above the position of first passage 101 openings of valve gear reception room 102, the other end of this second channel 103 is at suction passage 60 openings, communication valve means reception room 102 and suction passage 60.These first and second path 10s 1,103 and valve gear reception room 102 are formed in the lower support member 56, and they constitute above-mentioned access 100.But easy on and off is accommodated the valve gear 106 that works as safety valve movably in valve gear reception room 102.End ground at the spring 107 of this contact retractable above valve gear 106 is provided with, and the other end of this spring 107 is fixed in seal 104, towards the below valve gear 106 is applied elastic force often with spring 107 thus.
In addition, when valve gear 106 is between the aperture position of the aperture position of first passage 101 shown in Figure 4 and second channel 103, along the direction of depressing towards the below valve gear 106 is applied power by pressure (low pressure LP) in the suction passage 60 and spring 107, intermediate pressure applies power from first passage 101 towards the direction of lifting valve gear 106. promptly, in valve gear reception room 102, moves up and down by the refrigerant gas of the low pressure of the cold-producing medium suction side of the elastic force that has merged spring 107 pressure official post valve gear 106 with the refrigerant gas of the intermediate pressure of cold-producing medium discharge side.
In addition, in the present embodiment, when the pressure differential of the refrigerant gas of the refrigerant gas of low pressure and intermediate pressure during less than 5MPa, be contained in valve gears 106 in the valve gear reception room 102 and become the state of Fig. 2, be positioned at 103 of the other end of first passage 101 of valve gear reception room 102 and second channels, so cold-producing medium suction side and cold-producing medium are discharged side to can't help valve gear 106 inaccessible communicatively.
The elastic force of setting spring 107, make when middle pressure rise the refrigerant gas that makes low pressure and intermediate pressure refrigerant gas pressure differential expansion and when reaching 5MPa (higher limit), valve gear 106 is raised to the top of second channel 103 by the refrigerant gas of the intermediate pressure that flows into from first passage 101, make first passage 101 be communicated with (access 100 is communicated with) with second channel 103, thereby the refrigerant gas that makes cold-producing medium discharge the intermediate pressure of side flow into the suction passage 60 of cold-producing medium suction side.Pressure differential as both is littler than 5MPa, and then valve gear 106 drops to the connection position of first passage 101 and being communicated with between the position of second channel 103 of second channel 103 belows, inaccessible first passage 101 and second channel 103, thereby with access 100 obturations.Like this, discharging side as the cold-producing medium of the first revolution compression unit 32 presses with the level of the first order of the pressure differential of cold-producing medium suction side and becomes lower than higher limit.
Above-mentioned lower cover 68 is made of the circular steel plate of annular, is fixed in lower support member 56 by kingbolt 129 from the below with periphery, by the lower openings portion of tap 41 obturations with the discharge anechoic room 64 of lower cylinder 40 internal communication of the first revolution compression unit 32.The front end screw engagement of this kingbolt 129 is to upper support member 54.Fig. 5 illustrate lower support member 56 below, symbol 128 is to open and close the dump valve that first of tap 41 turns round compression unit 32 in discharging anechoic room 64.
Electrodynamic element 14 sides of discharging the upper cap 66 in anechoic room 64 and the closed container 12 are that not shown access is communicated with by the hole that connects upper and lower air cylinders 38,40 and central dividing plate 36.In this occasion, erect in the upper end of access be provided with in the middle of discharge pipe 121, the cold-producing mediums of discharge intermediate pressures in 12 from this centre discharge pipe 121 towards closed container.
In addition, upper cap 66 obturations are communicated to the top peristome of discharge anechoic room 62 of upper cylinder 38 inside of the second revolution compression unit 34 by tap 39, will be divided in the closed container 12 and discharge anechoic room 62 and electrodynamic element 14 sides.The circular steel plate of the cardinal principle annular in the hole that this upper cap 66 is connected by the bearing 54A that forms above-mentioned upper support member 54 as shown in Figure 6 constitutes, periphery by kingbolt 78 from upper fixed in upper support member 54.The front end screw engagement of this kingbolt 78 is in lower support member 56.As shown in Figure 6, symbol 127 is the dump valve that opens and closes the second revolution compression unit 34 of tap 39 in discharging anechoic room 62.
Dump valve 127,128 is made of elastic components such as lengthwise metallic plates, one side joint of dump valve 127,128 contacts tap 39,41 fluid-tight engagement, simultaneously, opposite side is fixed to the not shown screw hole that exists predetermined distance ground to be provided with tap 39,41 by not shown screw.Dump valve 127,128 touches tap 39,41 by certain power, but by the inaccessible tap 39,41 in elastic force freely openable ground.
In Fig. 3, symbol 196 is the suction pipe arrangement of the first revolution compression unit 32, and suction passage 60 ground that are communicated to lower support member 56 are installed.In addition, symbol 197 and 198 is the suction pipe arrangement and the discharge pipe arrangement of the second revolution compression unit 34, and an end that sucks pipe arrangement 197 is communicated in the closed container 12 at upper cap 66 upsides, and the other end is communicated to the suction passage 58 of the second revolution compression unit 34.Discharging pipe arrangement 198 installs to the discharge anechoic room 62 of the second revolution compression unit 34 communicatively.
In this occasion, as cold-producing medium, use and do not destroy earth environment, consider the above-mentioned carbon dioxide (CO as the nature cold-producing medium such as combustibility and toxicity 2), for example use existing oil such as mineral oil, alkylbenzene oil, ether oil, ester oil as the oil of lubricating oil.
Constitute explanation action by above below.When by terminal 20 and not shown distribution during to stator coil 28 energisings of electrodynamic element 14, electrodynamic element 14 startings make rotor 24 revolutions.Make up-down roller 46, the 48 eccentric revolution in upper and lower air cylinders 38,40 that is coupled to the eccentric part up and down 42,44 that is provided with integratedly with gyroaxis 16 by this revolution.
Like this, the cold-producing medium of low pressure (LP) of low-pressure chamber side that is drawn into lower cylinder 40 via the inlet hole 162 of the suction passage 60 that sucks pipe arrangement 196 and be formed at lower support member 56 figure below the lower cylinder 40 that is shown in Fig. 7 is by the action compresses of bottom roll 48 and lower blade 52, become intermediate pressure (MP), be discharged to tap 41 and be formed at the discharge anechoic room 64 of lower support member 56 from the hyperbaric chamber side of lower cylinder 40.
At this moment, discharge the pressure differential of the interior refrigerant gas of the discharge anechoic room 64 of side less than 5MPa as refrigerant gas in the suction passage 60 of cold-producing medium suction side and cold-producing medium, then the first passage 101 of valve gear 106 in valve gear reception room 102 and second channel 103 is communicated with between the position, so access 100 is by inaccessible.The refrigerant gas that is discharged to the intermediate pressure of discharging anechoic room 64 is discharged in the closed container 12 from middle discharge pipe 121 via not shown access.Make thus in the closed container 12 and become intermediate pressure.
Here, for example outside air temperature rises, the evaporating temperature of evaporimeter described later is uprised, intermediate pressure is uprised, the pressure differential of the refrigerant gas in the refrigerant gas in the suction passage 60 of low-pressure side and the discharge anechoic room 64 of intermediate pressure side reaches above-mentioned higher limit 5MPa, then valve gear 106 is raised to the top of the connection position of the second channel 103 in the valve gear reception room 102 by this higher intermediate pressure, so, first passage 101 is communicated with second channel 103, and the refrigerant gas of intermediate pressure flow into the suction passage 60 of low-pressure side.The pressure differential that makes both by the outflow towards the suction side (release) of this intermediate pressure refrigerant is during less than 5MPa, valve gear 106 turns back to the below of the connection position of second channel 103, like this, access 100 (first passage 101, valve gear reception room 102, and second channel 103) is by valve gear 106 obturations.
The refrigerant gas of the intermediate pressure in the closed container 12 enters into the suction passage 58 that is formed at upper support member 54 by sucking pipe arrangement 97 in closed container 12, be drawn into the low-pressure chamber side of upper cylinder 38 via the inlet hole 161 of the figure above the upper cylinder 38 that is shown in Fig. 8 of this place.The refrigerant gas of the intermediate pressure that sucks carries out second level compression by the action of last cylinder 46 and blade 50, become the refrigerant gas (HP) of HTHP, flow into the not shown radiator of being located at multi-stage compression formula rotary compressor 10 outsides from the discharge anechoic room 62 that is formed at upper support member 54 by discharging pipe arrangement 198 by tap 39 from the hyperbaric chamber side.Then, flow into not shown expansion valve, evaporimeter successively from radiator.
Like this, multi-stage compression formula rotary compressor 10 has electrodynamic element 14 and driven by electrodynamic element 14 in closed container 12 the first and second revolution compression units 32,34, the refrigerant gas of being discharged by the first revolution compression unit, 32 compression backs attracted to the second revolution compression unit 34, discharges after compression; Wherein, be provided with the cold-producing medium suction side and cold-producing medium access 100 of discharging side and the valve gear 106 that opens and closes access 100 that are communicated with the first revolution compression unit 32, valve gear 106 reaches set upper limit value (5MPa) when above in the pressure differential of cold-producing medium suction side and the cold-producing medium discharge side of the first revolution compression unit 32, open communication road 100, so, the differential pressure of the first order can be suppressed to below the higher limit.Like this, the dump valve 127 inside and outside pressure differentials of the first revolution compression unit 32 can be suppressed to below the higher limit, can avoid the problem of pressure official post dump valve 127 breakages.
In addition, in an embodiment, the inaccessible opening surface that constitutes the lower cylinder 40 of the first revolution compression unit 32, and will be formed in the suction passages 60 in the lower support member 56 of bearing of gyroaxis 16 and discharge anechoic rooms 64 and be communicated with electrodynamic element 14 by being formed at access 100 in the lower support member 56, simultaneously, valve gear 106 also is located in the lower support member 56, so, can access 100 and valve gear 106 is intensive in lower support member 56 and miniaturization. in addition, in lower support member 56, form access 100 in advance, valve gear 106 can be installed to this place installs, so, can improve the assembling operation of multi-stage compression formula rotary compressor 10.
Embodiment has illustrated gyroaxis 16 as the vertical multi-stage compression formula rotary compressor 10 of putting type, but the present invention also can be adapted to certainly with the horizontal type multi-stage compression formula rotary compressor of gyroaxis as horizontal arrangement type.In addition, also be not limited thereto, can suitably set corresponding to the capacity of rotary compressor and working pressure etc. by the higher limit of the level differential pressure of the first order shown in the embodiment.
In addition, by two stage compression type rotary compressors multi-stage compression formula rotary compressor has been described with first and second revolution compression units, but be not limited thereto, also the revolution compression unit can be applicable to have 3 grades, the multi-stage compression formula rotary compressor of 4 grades or more multistage revolution compression unit.
Figure 10 illustrates the skiagraph of bosom pressure-type multistage (secondary) compression type rotary compressor with first and second revolution compression units 32,34 as the embodiment of multi-stage compression formula rotary compressor of the present invention.
In this Figure 10, symbol 10 is with the bosom pressure-type multi-stage compression formula rotary compressor of carbon dioxide as cold-producing medium, the closed container 12 that this multi-stage compression formula rotary compressor 10 is made of steel plate, electrodynamic element 14, and rotary compressor structure portion 18 constitute; Closed container 12 is made of bowl-shape end cap (lid) 12B that is substantially of the upper opening of cylindrical container body 12A and inaccessible this vessel 12A; 14 configurations of this electrodynamic element are contained in the vessel 12A inner space upside of this closed container 12, and this rotary compressor structure portion 18 comprises and is disposed at these electrodynamic element 14 downsides and turns round compression unit 34 (second level) by the first revolution compression unit 32 (first order) and second that the gyroaxis 16 of electrodynamic element 14 drives.Closed container 12 with the bottom as oil groove.In addition, be formed centrally circular installing hole 12D on above-mentioned end cap 12B, the terminal (having omitted distribution) 20 that is used to feed electrical power to electrodynamic element 14 is installed at this installing hole 12D.
In addition, in the upper cap 66 of the second revolution compression unit 34, access 200 of the present invention is set.This access 200 is the passage of discharging the discharge anechoic room 62 of side in the closed container 12 with the cold-producing mediums of the second revolution compression unit for the path of passing through that is communicated with the intermediate pressure refrigerant gas that is compressed by the first revolution compression unit 32, as shown in Figure 11, one end of horizontally extending first passage 201 is communicated in the closed container 12, and the other end of first passage 201 is linked valve gear reception room 202.This valve gear reception room 202 is the hole that connects upper cap 66 along vertical direction, valve gear reception room 202 top at closed container 12 openings, and followingly discharging anechoic room 62 openings.In addition, the upper and lower opening of this valve gear reception room 202 is respectively by seal 203,204 obturations.
The second channel 205 of communication valve means reception room 202 and discharge anechoic room 62 is set at the seal 204 of being located at valve gear reception room 202 bottoms.By these first passages 201, valve gear reception room 202, and second channel 205 constitute access 200.In addition, in the valve gear reception room 202 of this access 200, accommodate spherical valve gear 207, an end of the spring 206 (elastic force applies member) of retractable is set contiguously above the valve gear 207 at this.The other end of this spring 206 is fixed on the seal 203 of upside, and valve gear 207 applies elastic force towards downside often by this spring 206, often with second channel 205 obturations.
The cold-producing medium of the intermediate pressure in the closed container 12 flow in the valve gear reception room 202 from first passage 201, towards downside valve gear 207 is applied elastic force, simultaneously, the cold-producing medium of discharging the high pressure in the anechoic room 62 flow in the valve gear reception room 202 from the second channel 205 of the seal 204 of being located at downside, from the following side that faces up of valve gear 207 valve gear 207 is applied power.
Like this, to be upside from a side of spring 206 contact apply power by the refrigerant gas of intermediate pressure and spring 206 towards downside with valve gear 207, applies power by the refrigerant gas of high pressure towards upside from opposition side.The following second channel 205 that touches often of valve gear 207 is and airtight, and like this, access 200 is by valve gear 207 obturations.
The elastic force of setting spring 206, make the pressure differential of refrigerant gas and the refrigerant gas of discharging the high pressure in the anechoic room 62 of the intermediate pressure in closed container 12 reach higher limit for example during 8MPa, being contacted with second channel 205 airtight valve gears 207 is lifted towards the top by the higher pressure refrigerant gas that flows into from second channel 205. therefore, above-mentioned pressure differential is the above occasion of 8MPa (higher limit), be communicated to first passage 201 and second channel 205 by valve gear reception room 202, the higher pressure refrigerant gas of discharging in the anechoic room 62 flow out in the closed container 12. when above-mentioned pressure differential narrows down to when being lower than 8MPa, spring 206 makes valve gear 207 touch second channel 205 and is airtight, first passage 201 and second channel 205 are by valve gear 207 obturations. and like this, avoid partial level differential pressure to become excessive in advance.
Like this, become intermediate pressure from the low pressure refrigerant that inlet hole 162 is drawn into the low-pressure chamber side of lower cylinder 40 by the action compresses of bottom roll 48 and lower blade 52 as shown in Figure 7 via the suction passage 60 that is formed at lower support member 56, be discharged in the closed container 12 from middle discharge pipe 121 via not shown access from the tap 41 of the hyperbaric chamber side of lower cylinder 40 and the discharge anechoic room 64 that is formed at lower support member 56.
The refrigerant gas of the intermediate pressure in the closed container 12 is drawn into the low-pressure chamber side of upper cylinder 38 as shown in Figure 8 from inlet hole 161 via the suction passage 58 that is formed at upper support member 54 through not shown coolant channel.The refrigerant gas of the intermediate pressure that sucks carries out second level compression by the action of last cylinder 46 and blade 52, becomes the refrigerant gas of HTHP, is discharged to the discharge anechoic room 62 that is formed at upper support member 54 by tap 39 from the hyperbaric chamber side.
At this moment, as the pressure differential of the refrigerant gas of the intermediate pressure in the closed container 12 and the refrigerant gas of discharging the high pressure in the anechoic room 62 less than 8MPa, then as described above, valve gear 207 is contacted with second channels 205 in the valve gear reception room 202 and airtight, access 200 is not open, and the refrigerant gas that is discharged to the high pressure of discharging anechoic room 62 all flow into the not shown radiator of being located at multi-stage compression formula rotary compressor 10 outsides by coolant channel.
The cold-producing medium that flow into radiator here dispels the heat and has given play to heat effect.The cold-producing medium that comes out from radiator by not shown decompressor decompression after, enter into the also unshowned evaporimeter of figure, there evaporation.Finally be drawn into the suction passage 60 of the first revolution compression unit 32, and carry out this circulation repeatedly.
Here, descend and when the evaporating temperature of the cold-producing medium of above-mentioned evaporimeter was descended, as described above, the pressure (intermediate pressure) that is discharged to the cold-producing medium in the closed container 12 from the first revolution compression unit 32 also was difficult to rise when outside air temperature.Like this, when the refrigerant gas of the intermediate pressure in the closed container 12 reaches 8MPa with the pressure differential of discharging the higher pressure refrigerant gas in the anechoic room 62, by the pressure of discharging in the anechoic room 62 the valve gear 207 resistance springs 206 that are contacted with second channel 205 are lifted, leave from second channel 205, so, first passage 201 is communicated with second channel 205, and the refrigerant gas of high pressure flow in the closed container 12 of intermediate pressure side.In addition, when both pressure differential descends and when being lower than 8MPa, valve gear 207 is contacted with second channel 205 and airtight, like this, second channel 205 is by valve gear 207 obturations.
Like this, the first and second revolution compression units 32,34 that in closed container 12, have electrodynamic element 14 and drive by this electrodynamic element 14, refrigerant gas by the intermediate pressure after 32 compressions of the first revolution compression unit attracted to the second revolution compression unit 34, discharges after compression; Wherein, the cold-producing medium that passes through the path and the second revolution compression unit 34 that is provided with the refrigerant gas of the intermediate pressure after connection is compressed by the first revolution compression unit 32 is discharged side access 200 that is communicated with and the valve gear 207 that opens and closes this access 200, it is that 8MPa is when above that the pressure differential that this valve gear 207 is discharged the refrigerant gas of side at the cold-producing medium of the refrigerant gas of intermediate pressure and the second revolution compression unit 34 is in the set upper limit value, open communication road 200, so, can with partial differential constrain make lowlyer than higher limit, can avoid the breakage of the dump valve 128 of the second revolution compression unit 34 in advance.
In addition, having formation second turns round the discharge anechoic room 62 of the upper cylinder 38 of compression unit 34, discharge refrigerant compressed gas in this upper cylinder 38, reaches as the upper cap 66 that surrounds the wall of this discharge anechoic room 62, access 200 is formed in the upper cap 66, be communicated with in the closed container 12 and discharge anechoic room 62, valve gear 207 is located in the upper cap 66, so, access 200 is not formed complicated structure and can suppress partial level differential pressure.
Embodiment has illustrated gyroaxis 16 as the vertical multi-stage compression formula rotary compressor 10 of putting type, but the present invention also can be adapted to certainly with the horizontal type compression type rotary compressor of gyroaxis as horizontal arrangement type.
In addition, by two stage compression type rotary compressors multi-stage compression formula rotary compressor has been described with first and second revolution compression units, but be not limited thereto, also the revolution compression unit can be applicable to have 3 grades, the multi-stage compression formula rotary compressor of 4 grades or more multistage revolution compression unit.
In an embodiment, valve gear 207 as spherical valve gear, but is not limited thereto, also can be used as valve gear cylindraceous 217 as shown in Figure 12.In this occasion, the wall ground that valve gear 217 is contacted with valve gear reception room 202 is provided with, usually, in the valve gear reception room 202 between first passage 201 and second channel 205, inaccessible access 200.In the occasion that pressure differential is crossed 8MPa, valve gear 217 is communicated with first passage 201 by the top that is raised to first passage 201 with second channel 205, and the refrigerant gas of high pressure flow in the closed container 12 of intermediate pressure.Both pressure differentials are during less than 8MPa, and valve gear 217 turns back to the below of first passage 201, and first passage 201 and second channel 205 are by valve gear 217 obturations.
Figure 13 has the skiagraph of multistage (secondary) compression type rotary compressor 10 of the first and second revolution compression units 32,34 for the embodiment as multi-stage compression formula rotary compressor of the present invention illustrates, Figure 14 is the amplification profile diagram of pressure-regulating valve 107 parts of rotary compressor 10, Figure 15 is the front elevation of rotary compressor 10, and Figure 16 is the side view of rotary compressor 10.
In the figure, symbol 10 is with carbon dioxide (CO 2) as the bosom pressure-type multi-stage compression formula rotary compressor of cold-producing medium, the closed container cylindraceous 12 that this rotary compressor 10 is made of steel plate, electrodynamic element 14, and rotary compressor structure portion 18 constitute, this electrodynamic element 14 is disposed at this closed container 12 inner space upsides, and this rotary compressor structure portion 18 comprises that the first revolution compression unit 32 (first order) and second that the gyroaxis 16 by electrodynamic element 14 that is disposed at these electrodynamic element 14 downsides drives turns round compression unit 34 (second level).
Closed container 12 with the bottom as oil groove, bowl-shape end cap (lid) 12B that is substantially by the upper opening of the vessel 12A that accommodates electrodynamic element 14 and rotary compressor structure portion 18 and inaccessible this vessel 12A constitutes, and, be formed centrally circular installing hole 12D on this end cap 12B, the terminal (having omitted distribution) 20 that is used to feed electrical power to electrodynamic element 14 is installed at this installing hole 12D.
Electrodynamic element 14 is mounted to the stator 22 of ring-type and in the inboard of this stator 22 some rotors that insert configuration with gap 24 is set by the inner peripheral surface along closed container 12 upper spaces and constitutes.This rotor 24 is fixed on the gyroaxis 16 that extends along by the vertical direction at center.
Stator 22 have layered product 26 that the electromagnetic steel plate of the ring-type of laminating obtains and with string around (concentrate and reel) mode package in the stator coil 28 of the tooth portion of this layered product 26.In addition, rotor 24 is also similarly formed by the layered product 30 of electromagnetic steel plate with stator 22, inserts permanent magnet MG in this layered product 30.
Clamping central dividing plate 36. these the first revolution compression units 32 and the second revolution compression unit 34 are by central dividing plate 36 between the above-mentioned first revolution compression unit 32 and the second revolution compression unit 34, be disposed at the upper cylinder 38 up and down of this central dividing plate 36, lower cylinder 40, with the eccentric part up and down 42 of being located at gyroaxis 16 with having 180 degree phase differences, 44 join and are incorporated in upper and lower air cylinders 38, carry out eccentric rotating up-down roller 46 in 40,48, be contacted with this up-down roller 46,48 with upper and lower air cylinders 38, be divided into the blade up and down 50 of low-pressure chamber side and hyperbaric chamber side in 40 respectively, 52, reach upper support member 54 and lower support member 56 formations that inaccessible upper cylinder 38 upside opening surfaces and lower cylinder 40 open lower side faces are also used as the bearing of gyroaxis 16 as supporting member.
The eliminating volume of the first revolution compression unit 32 is set at eliminating volume * 100%=40%-75% that second eliminating volume/first that turns round compression unit 34 turns round compression unit 32 with the ratio of the eliminating volume of the second revolution compression unit 34.
Forming the gathering sill 70 of accommodating above-mentioned blade 50 in the upper cylinder 38 that constitutes the above-mentioned second revolution compression unit 34 as shown in Figure 14, is that the rear side of blade 50 forms the resettlement section 70A that accommodates as the spring 74 of spring member in the outside of this gathering sill 70.This spring 74 is contacted with the rear side end of blade 50, towards cylinder 46 sides blade 50 is applied elastic force often.This resettlement section 70A is at gathering sill 70 sides and closed container 12 (vessel 12A) side opening, in closed container 12 sides of the spring 74 that is contained in resettlement section 70A metal latch 137 is set, and plays the anticreep effect of spring 74.In addition, unshowned sealing ring in the installation diagram between the side face of latch 137 is for the inner face that seals this latch 137 and resettlement section 70A.
In addition gathering sill 70 between the 70A of resettlement section in order towards cylinder 46 sides blade 50 to be applied elastic force with spring 74 often, the cold-producing medium discharge pressure that is provided with the second revolution compression unit 34 is added to the back pressure chamber 99 of blade 50.This back pressure chamber 99 is communicated to second channel 106 described later.
In addition, the suction passage 60 (suction passage of upside does not illustrate in the drawings) and the discharge anechoic room 62,64 that are communicated to the inside of upper and lower air cylinders 38,40 by not shown inlet hole respectively are set, thereby this discharge anechoic room 62,64 is by making part depression and by upper cap 66, lower cover 68 this depressed part obturation being formed in upper support member 54 and lower support member 56.
Discharge in anechoic room 64 and the closed container 12 and be communicated with by the access that connects upper and lower air cylinders 38,40 and central dividing plate 36, the upper end of access is upright establish in the middle of discharge pipe 121, to closed container 12 in, discharge the refrigerant gas that turns round the intermediate pressure that compression unit 32 compresses by first from this centre discharge pipe 121.
Obturation will be separated into discharge anechoic room 62 and electrodynamic element 14 sides with the upper cap 66 of the top peristome of the discharge anechoic room 62 of upper cylinder 38 internal communication of the second revolution compression unit 34 in the closed container 12.
In addition, in upper support member 54, form access 100.This access 100 is for being communicated with the discharge anechoic room 62 that links to each other with the not shown tap of the upper cylinder 38 of the second revolution compression unit 34 and the passage of back pressure chamber 99, as shown in Figure 14, comprise along up/down perforation upper support member 54 and upside by the valve reception room 102 of upper cap 66 obturations, be communicated with the upper end of this valve reception room 102 and discharge the first passage 101 of anechoic room 62 and be positioned at valve reception room 102 outsides and be communicated with the second channel 106 of this valve reception room 102 and back pressure chamber 99.
Above-mentioned valve reception room 102 is the hole cylindraceous of extending along vertical direction, and the lower end is by seal 103 obturations.In the lower end of the upside mounting spring member 104 (helical springs) of seal 103, valve body 105 is installed in the upper end of this spring member 104.But these valve body 105 easy on and off are located in the valve reception room 102 movably, and the perisporium ground that can be contacted with this valve reception room 102 is separated valve reception room 102 edges up and down with being free to slide.Constitute pressure-regulating valve 107 of the present invention by these valve bodies 105 and spring member 104.
Back pressure chamber 99 ground of above-mentioned second channel 106 from the position of valve reception room 102 lower end specified altitudes to the below form, access 100 was closed when above-mentioned valve body 105 was in second channel 106 tops, when the below of arrival second channel 106 upper ends above the valve body 105, access 100 is open.Above-mentioned spring member 104 applies elastic force towards the direction of lifting this valve body 105 often.
In addition, valve body 105 accepts to flow into from first passage 101 power of the direction that the refrigerant gas of the high pressure in the valve reception room 102 depresses from the top, accept the power of the direction lifted from the below by the pressure in the back pressure chamber 99 from second channel 106. promptly, compression in the upper cylinder 38 of the second revolution compression unit 34 moves up and down valve body 105 by the pressure in the elastic force+back pressure chamber 99 of pressure that is discharged to the refrigerant gas of discharging anechoic room 62 and spring member 104 in valve reception room 102.
The elastic force of this spring member 104 is for example when the pressure differential of discharging anechoic room 62 and back pressure chamber 99 (discharging the pressure of the pressure-back pressure chamber 99 of anechoic room 62) is for example big than 2MPa, depress the top upper end from second channel 106 of valve body 105, open communication road 100, when pressure differential is reduced to 2MPa when following, valve body 105 is lifted, rise to the top of the upper end of second channel 106 above it, close access 100.
In this occasion, as cold-producing medium, use and do not destroy earth environment, consider the above-mentioned carbon dioxide (CO as the nature cold-producing medium such as combustibility and toxicity 2), for example use mineral oil, alkylbenzene oil, ether oil, ester oil, PAG existing oil such as (PAGs) as the oil of lubricating oil.
At the side and the suction passage 60 (upside is not shown) upper support member 54 and lower support member 56 of the vessel 12A of closed container 12, discharge anechoic room 62, and the corresponding position of upside (position corresponding substantially) of upper cap 66 with the lower end of electrodynamic element 14, weld fixed sleeving 141,142,143 respectively, reach 144.Sleeve pipe 141 and sleeve pipe adjacency about in the of 142, simultaneously, sleeve pipe 143 is positioned on the big body diagonal of sleeve pipe 141.In addition, sleeve pipe 144 is positioned at the position of staggering 90 degree substantially with sleeve pipe 141.
Insertion connects an end that refrigerant gas is directed into the cold-producing medium ingress pipe 92 of upper cylinder 38 in sleeve pipe 141, and an end of this cold-producing medium ingress pipe 92 is communicated to the not shown suction passage of upper cylinder 38.This cold-producing medium ingress pipe 92 arrives sleeve pipe 144 by the upside of closed container 12, thereby other end insertion is connected to sleeve pipe 144 interior being communicated in the closed container 12.
In addition, insertion connects an end that refrigerant gas is directed into the cold-producing medium ingress pipe 94 of lower cylinder 40 in sleeve pipe 142, and an end of this cold-producing medium ingress pipe 94 is communicated to the suction passage 60 of lower cylinder 40.The other end of this cold-producing medium ingress pipe 94 is connected to the lower end of reservoir 146.In addition, insert connection refrigerant discharge leader 96 in sleeve pipe 143, an end of this refrigerant discharge leader 96 is communicated to discharges anechoic room 62.
Above-mentioned reservoir 146 is the storage tank of the gas-liquid separation that is used to suck cold-producing medium, and the carriage 148 by the reservoir side is installed to the carriage 147 of closed container side of the upper side of the vessel 12A that is fixedly welded on closed container 12.
The rotary compressor 10 of present embodiment is used for the refrigerant loop of hot water supply apparatus 153 as shown in Figure 17.The refrigerant discharge leader 96 that is rotary compressor 10 is connected to the inlet that water heats the gas cooler 154 of usefulness.This gas cooler 154 is arranged at the not shown hot water storage tank of hot water supply apparatus 153.The pipe arrangement that comes out from gas cooler 154 passes through the inlet that arrives evaporimeters 157 as the expansion valve 156 of decompressor, and the outlet of evaporimeter 157 is connected to cold-producing medium ingress pipe 94.In addition, from the middle part of cold-producing medium ingress pipe 92 as shown in Figure 17 branch constitute the defrosting pipe 158 of defrost circuit, be connected in the refrigerant discharge leader 96 of the inlet that arrives gas cooler 154 by magnetic valve 159 as the stream control device.In Figure 17, omitted reservoir 146.
Constitute explanation action by above below.In service in common heating, magnetic valve 159 cuts out.When by terminal 20 and not shown distribution the stator coil 28 of electrodynamic element 14 being switched on, electrodynamic element 14 startings make rotor 24 revolutions.Make up-down roller 46, the 48 eccentric revolution in upper and lower air cylinders 38,40 that is coupled to the eccentric part up and down 42,44 that is wholely set with gyroaxis 16 by this revolution.
Like this, (first order suction pressure: cold-producing medium 4MPa) is by the action compresses of bottom roll 48 and blade 52 to be drawn into the low pressure of the low-pressure chamber side of lower cylinder 40 via cold-producing medium ingress pipe 94 and the suction passage 60 that is formed at lower support member 56 from not shown inlet hole, become intermediate pressure (first order discharge pressure: 8MPa), the discharge anechoic room 64. that is discharged to not shown tap and is formed at lower support member 56 from the hyperbaric chamber side of lower cylinder 40 is discharged to the refrigerant gas of discharging the intermediate pressure in the anechoic room 64 and is discharged in the closed container 12 from middle discharge pipe 121 through above-mentioned access, and making thus becomes intermediate pressure (8MPa) in the closed container 12.
The refrigerant gas of the intermediate pressure of closed container 12 comes out from sleeve pipe 144, via cold-producing medium ingress pipe 92 and the not shown suction passage that is formed at upper support member 54, is drawn into the low-pressure chamber side of upper cylinder 38 from not shown inlet hole.The refrigerant gas of the intermediate pressure that sucks carries out second level compression by the action of last cylinder 46 and blade 50, become the refrigerant gas (second level discharge pressure: 12MPa), be discharged to the discharge anechoic room 62 that is formed in the upper support member 54 by not shown tap of HTHP from the hyperbaric chamber side.
Being discharged to the refrigerant gas of discharging anechoic room 62 flow in the gas cooler 154 via refrigerant discharge leader 96.The refrigerant temperature of this moment is raised to substantially+and 100 ℃, the heat radiation of the refrigerant gas of this HTHP to the heating of the water in the hot water storage tank, generates approximately+90 ℃ hot water.
On the other hand, in gas cooler 154, self is cooled off cold-producing medium, comes out from gas cooler 154.After expansion valve 156 decompressions, flow into evaporimeter 157 evaporations, be drawn in the first revolution compression unit 32 from cold-producing medium ingress pipe 94 through reservoir 146 (not shown in Figure 17), and carry out this circulation repeatedly.
In service in such heating, pressure in the discharge anechoic room 62 become the high pressure about 12MPa as described above, but at this moment, the pressure that pressure ratio in the back pressure chamber 99 is discharged in the anechoic room 62 is low, when its difference is bigger than 2MPa, as described above, the valve body 105 open communication roads 100 of pressure-regulating valve 107.Like this, the refrigerant gas of the high pressure in the discharge anechoic room 62 flow in the back pressure chamber 99.
Importing the pressure that makes in the back pressure chamber 99 by this pressure rises, when the pressure in the back pressure chamber 99 was reduced to 2MPa with the difference of discharging the pressure in the anechoic room 62, as described above, the valve body 105 of pressure-regulating valve 107 was closed access 100, so refrigerant gas stops to the inflow of back pressure chamber 99.
Like this, in second level discharge pressure is the occasion of 12MPa, pressure in the back pressure chamber 99 maintains than intermediate pressure 8MPa height, than the low about 10MPa of second level discharge pressure 12MPa, so, can prevent that so-called blade from takeofing and add the back pressure that exceeds more than the needs at blade 50, makes blade 50 put on the power optimization of cylinder 46.Like this, can alleviate the burden of the slipper that is added in blade 50 front ends and last cylinder 46 peripheries, can improve the durability of blade 50 and last cylinder 46, avoid the breakage of blade 50 and last cylinder 46 in advance.
Particularly under the environment of low outside air temperature, such heating operation makes in evaporimeter 157 frostings.In this occasion, open magnetic valve 159, expansion valve 156 becomes full-gear, implements the Defrost operation of evaporimeter 157.Like this, the cold-producing medium of the intermediate pressure in the closed container 12 (comprising a spot of high-pressure refrigerant of discharging from the second revolution compression unit 34) arrives gas cooler 154 by defrosting pipe 158.The temperature of this cold-producing medium is+50-+60 ℃ about, do not dispel the heat at gas cooler 154, become the initial form that absorbs heat on the contrary by cold-producing medium.The cold-producing medium of discharging from gas cooler 154 arrives evaporimeter 157 by expansion valve 156.That is, do not reduce pressure, in fact directly supply with the higher cold-producing medium of temperature of intermediate pressure substantially to evaporimeter 157, heating fumigators 157 thus, defrost.
Like this, the first and second revolution compression units 32,34 that in closed container 12, have electrodynamic element 14 and drive by electrodynamic element 14, be discharged in the closed container 12 by the refrigerant gas after 32 compressions of the first revolution compression unit, the refrigerant gas of the intermediate pressure of this discharge is by 34 compressions of the second revolution compression unit; Wherein, have the upper cylinder 38 that is used to constitute the second revolution compression unit 34 and with the last eccentric part 42 of the gyroaxis 16 that is formed at electrodynamic element 14 join be incorporated in carry out in the upper cylinder 38 off-centre rotating on cylinder 46, be contacted with cylinder 46 on this and will be divided into the blade 50 of low-pressure chamber side and hyperbaric chamber side in the upper cylinder 38, be used for often cylinder 46 sides up apply power to this blade 50 back pressure chamber 99, the cold-producing medium that is communicated with the second revolution compression unit 34 is discharged the access 100 of side and back pressure chamber 99, adjustment is added to the pressure-regulating valve 107 of the pressure of back pressure chamber 99 by this access 100, so, the pressure of back pressure chamber 99 is maintained that the height of discharging side than the cold-producing medium of the second revolution compression unit 34 forces down and than the high setting of intermediate pressure in the closed container 12 by this pressure-regulating valve 107, thereby preventing that so-called blade from takeofing and preventing applies the back pressure that exceeds needs at blade 50, makes the upwards power optimization that applies of cylinder 46 of blade 50.
Like this, can alleviate the burden of the slipper that is added in blade 50 front ends and last cylinder 46 peripheries, can improve the durability of blade 50 and last cylinder 46, avoid the breakage of blade 50 and last cylinder 46 in advance.
Particularly owing in upper support member 54, form access 100, to discharge anechoic room 62 and back pressure chamber 99 connections, simultaneously, pressure-regulating valve 107 is set in upper support member 54, so, can effectively utilize the limited space in the closed container 12, and not make complex structureization can carry out pressure adjustment in the back pressure chamber 99 of blade 50.In addition, owing in upper support member 54, set in advance access 100 and pressure-regulating valve 107, so assembling operation is good.
Each force value is not limited thereto shown in the embodiment, also can suitably set according to the capacity and the ability of compressor.In addition, in an embodiment, having illustrated gyroaxis 16 is formed the vertical multi-stage compression formula rotary compressor 10 of putting type, is the multi-stage compression formula rotary compressor of horizontal arrangement type but the present invention also can be adapted to make gyroaxis certainly.
In addition, by two stage compression type rotary compressors multi-stage compression formula rotary compressor has been described with first and second revolution compression units, but be not limited thereto, also the revolution compression unit can be applicable to have 3 grades, the multi-stage compression formula rotary compressor of 4 grades or more multistage revolution compression unit.In addition, in an embodiment, multi-stage compression formula rotary compressor 10 is used for the refrigerant loop of hot water supply apparatus 153, but is not limited thereto, the present invention is also effective when being used for room heater etc.
Figure 18 illustrates the skiagraph of the rotary compressor 10 of bosom pressure-type multistage (secondary) compression with first and second revolution compression units 32,34 as the embodiment of multi-stage compression formula rotary compressor of the present invention.
The upper and lower air cylinders 38,40 that constitutes the second and first revolution compression unit 34,32 respectively is made of the material of same gauge in an embodiment.In addition, each internal diameter that constitutes as each upper and lower air cylinders 38,40 is carried out machining is D2, D1, then turn round the occasion of the eliminating volumetric ratio of compression units 32,34 in change first and second, get rid of volumetric ratio by changing the inside diameter D 1 of lower cylinder 40 of the above-mentioned first revolution compression unit 32, setting.
At for example thickness (highly) by changing lower cylinder 40 thus size is set the occasion of getting rid of volumetric ratio, must be with the material of lower cylinder 40, thickness (highly) size of eccentric part 44 and bottom roll 48 all changes down.That is,, need at least to change lower cylinder 40 and bottom roll 48, following eccentric part 44 is changed the machining of gyroaxises 16 from material in this occasion.On the other hand, in occasion of the present invention, the material of lower cylinder 40 remains unchanged at least, the internal diameter in the time of only need changing machining.In addition, identical although need change external diameter at least as internal diameter to bottom roll 48, then descend eccentric part 44 not change.Like this, according to the present invention, the material of lower cylinder 40 is constant at least, and only need change the external diameter of its machining and bottom roll 48 or only change the external diameter and the internal diameter of bottom roll 48 and change following eccentric part 44 can be corresponding.Like this, component change is suppressed to Min., can sets the eliminating volumetric ratio of the first and second best revolution compression units 32,34.In an embodiment, with more than 40% below 75% of the eliminating volume of eliminating volume settings to the first revolution compression unit 32 of the second revolution compression unit 34.
Like this, the low pressure refrigerant that is drawn into the low-pressure chamber side of lower cylinder 40 via cold-producing medium ingress pipe 94 and the suction passage 60 that is formed at lower support member 56 from not shown inlet hole becomes intermediate pressure by the action compresses of cylinder 48 and blade 52, is discharged in the closed container 12 from middle discharge pipe 121 through not shown access from the not shown tap of lower cylinder 40 hyperbaric chamber sides, the discharge anechoic room 64 that is formed at lower support member 56.Make thus in the closed container 12 and become intermediate pressure.
The refrigerant gas of the intermediate pressure in the closed container 12 is from sleeve pipe 144 come out to be drawn into from not shown inlet hole via cold-producing medium ingress pipe 92 and the not shown suction passage that the is formed at upper support member 54 low-pressure chamber side of upper cylinder 38. and the refrigerant gas of the intermediate pressure of suction carries out second level compression by the action of last cylinder 46 and blade 50, become the refrigerant gas of HTHP, from the hyperbaric chamber side by not shown tap via the discharge anechoic room 62 that is formed at upper support member 54, refrigerant discharge leader 96 flow in the gas cooler 154. this moment refrigerant temperature be raised to substantially+100 ℃, the refrigerant gas heat radiation of this HTHP, water in the hot water storage tank is heated, generates+90 ℃ hot water approximately.
Like this, do not change thickness (highly) size of lower cylinder 40, only change the inside diameter D 1 of this lower cylinder 40, with the eliminating volume settings of the second revolution compression unit 34 is more than 40% below 75% of eliminating volume of the first revolution compression unit 32, thereby set the eliminating volumetric ratio of the first and second revolution compression units 32,34, so, can do one's utmost to suppress the variation of cylinder material and parts such as eccentric part, cylinder, reduce the compression load of the second revolution compression unit 34, obtained to do one's utmost to suppress the eliminating volumetric ratio of the best of level differential pressure.In addition, because the size up and down of rotary compressor structure portion 18 do not enlarge yet, so multi-stage compression formula rotary compressor 10 also can be realized miniaturization.
In an embodiment, upper and lower air cylinders 38,40 is formed same thickness (highly) size, but be not limited thereto, be also contained in original with regard to different thickness (highly) thus the state of size down the internal diameter of the cylinder by changing the first revolution compression unit set the occasion of getting rid of volumetric ratio.
In addition, embodiment has illustrated gyroaxis 16 has been formed the vertical multi-stage compression formula rotary compressor 10 of putting type, has been the multi-stage compression formula rotary compressor of horizontal arrangement type but the present invention also can be adapted to make gyroaxis certainly.In addition, by two stage compression type rotary compressors multi-stage compression formula rotary compressor has been described with first and second revolution compression units, but be not limited thereto, also the revolution compression unit can be applicable to have 3 grades, the multi-stage compression formula rotary compressor of 4 grades or more multistage revolution compression unit.
In addition, in an embodiment, multi-stage compression formula rotary compressor 10 is used for the refrigerant loop of hot water supply apparatus 153, but is not limited thereto, the present invention is also effective when being used for room heater etc.
Figure 19 illustrates the skiagraph of the rotary compressor 10 of bosom pressure-type multistage (secondary) compression with first and second revolution compression units 32,34 as the embodiment of rotary compressor of the present invention.
In the figure, symbol 10 is with CO 2(carbon dioxide) is as the bosom pressure-type multi-stage compression formula rotary compressor of cold-producing medium, the closed container cylindraceous 12 that this multi-stage compression formula rotary compressor 10 is made of steel plate, electrodynamic element 14, and rotary compressor structure portion 18 constitute, this electrodynamic element 14 is disposed at this closed container 12 inner space upsides, and this rotary compressor structure portion 18 comprises that the first revolution compression unit 32 (first order) and second that the gyroaxis 16 by electrodynamic element 14 that is disposed at these electrodynamic element 14 downsides drives turns round compression unit 34 (second level).
Closed container 12 with the bottom as oil groove, bowl-shape end cap (lid) 12B that is substantially by the upper opening of accommodating electrodynamic element 14 and the vessel 12A that accommodates rotary compressor structure portion 18 and inaccessible this vessel 12A constitutes, and, be formed centrally circular installing hole 12D on this end cap 12B, fixed the terminal (having omitted distribution) 20 that is used to feed electrical power to electrodynamic element 14 in this installing hole 12D welding.
Above-mentioned electrodynamic element 14 is mounted to the stator 22 of ring-type and in the inboard of this stator 22 some rotors that insert configuration with gap 24 is set by the inner peripheral surface along closed container 12 upper spaces and constitutes.Fixing the gyroaxis 16 that extends along by the vertical direction at center at this rotor 24.
Stator 22 constitutes around the stator coil 28 of (concentrate and reel) mode package in the tooth portion of this layered product 26 by the layered product 26 of the electromagnetic steel plate acquisition that laminates ring-type with string.In addition, rotor 24 constitutes by insert permanent magnet MG in the layered product 30 of electromagnetic steel plate.
Clamping central dividing plate 36 between the above-mentioned first revolution compression unit 32 and the second revolution compression unit 34.That is, first of the rotary compressor structure portion 18 revolution compression unit 32 and the second revolution compression unit 34 are by central dividing plate 36, be disposed at the upper cylinder 38 up and down of this central dividing plate 36, lower cylinder 40, with the eccentric part up and down 42 of being located at gyroaxis 16 with having 180 degree phase differences, 44 join and are incorporated in upper and lower air cylinders 38, carry out eccentric rotating up-down roller 46 in 40,48, be contacted with this up-down roller 46,48 with upper and lower air cylinders 38, be divided into the not shown blade up and down of low-pressure chamber side and hyperbaric chamber side in 40 respectively, reach upper support member 54 and lower support member 56 formations that inaccessible upper cylinder 38 upside opening surfaces and lower cylinder 40 open lower side faces are also used as the bearing of gyroaxis 16 as supporting member.
In addition, thus in upper support member 54 and lower support member 56, be provided with by inlet hole 161,162 be communicated to respectively upper and lower air cylinders 38,40 inside suction passage 58,60 and by make part depression and by upper cap 66, lower cover 68 with the inaccessible discharge anechoic room 62,64 that forms of this depressed part.
Discharge in anechoic room 64 and the closed container 12 and be communicated with by the not shown access that connects upper and lower air cylinders 38,40 and central dividing plate 36, the upper end of access is upright establish in the middle of discharge pipe 121, to closed container 12 in, discharge the refrigerant gas that turns round the intermediate pressure that compression unit 32 compresses by first from this centre discharge pipe 121.
Upper cap 66 is divided into the discharge anechoic room 62 of upper cylinder 38 internal communication with the second revolution compression unit 34, with upper cap 66 electrodynamic element 14 is set with forming predetermined distances above this upper cap 66.
As cold-producing medium, use and do not destroy earth environment, consider the above-mentioned CO as the nature cold-producing medium such as combustibility and toxicity here, 2(carbon dioxide) for example uses mineral oil, alkylbenzene oil, ether oil, ester oil, PAG existing oil such as (PAGs) as the oil of lubricating oil.
The side and the suction passage 58,60 upper support member 54 and lower support member 56 of the vessel 12A of closed container 12, discharge anechoic room 62, and upper cap 66 above (position corresponding substantially) corresponding position with the lower end of electrodynamic element 14 weld fixed sleeving 141,142,143 respectively, reach 144.Sleeve pipe 141 and sleeve pipe adjacency about in the of 142, simultaneously, sleeve pipe 143 is positioned on the big body diagonal of sleeve pipe 141.In addition, sleeve pipe 144 is positioned at the position of staggering 90 degree substantially with sleeve pipe 141.
Insert to connect the end as the cold-producing medium ingress pipe 92 of coolant channel that refrigerant gas is directed into upper cylinder 38 in sleeve pipe 141, an end of this cold-producing medium ingress pipe 92 is communicated to the suction passage 58 of upper cylinder 38.This cold-producing medium ingress pipe 92 arrives sleeve pipe 144 by the top of closed container 12, and the other end inserts and is connected in the sleeve pipe 144, thereby is communicated in the closed container 12.
In addition, insertion connects an end that refrigerant gas is directed into the cold-producing medium ingress pipe 94 of lower cylinder 40 in sleeve pipe 142, and an end of this cold-producing medium ingress pipe 94 is communicated to the suction passage 60 of lower cylinder 40.The other end of this cold-producing medium ingress pipe 94 is connected to the lower end of not shown reservoir.In addition, insert connection refrigerant discharge leader 96 in sleeve pipe 143, an end of this refrigerant discharge leader 96 is communicated to discharges anechoic room 62.
Above-mentioned reservoir is the storage tank that is used to suck the gas-liquid separation of cold-producing medium, is installed to the carriage 147 of the upper side of the vessel 12A that is fixedly welded on closed container 12 by the carriage of not shown reservoir side.
Figure 20 illustrates the refrigerant loop of the hot water supply apparatus 153 of having used the embodiment of the invention, and above-mentioned multi-stage compression formula rotary compressor 10 constitutes the part of the refrigerant loop of hot water supply apparatus 153 shown in Figure 20.That is, the refrigerant discharge leader 96 of multi-stage compression formula rotary compressor 10 is connected to the inlet of gas cooler 154, and this gas cooler 154 is located at the not shown hot water storage tank of hot water supply apparatus 153 for water being heated to generate hot water.The pipe arrangement that comes out from gas cooler 154 passes through the inlet that arrives evaporimeters 157 as the expansion valve 156 of first decompressor, and the outlet of evaporimeter 157 is connected to cold-producing medium ingress pipe 94 by above-mentioned reservoir (not shown in Figure 20).
In addition, branch out the defrosting pipe 158 that constitutes defrost circuit from being used for that the cold-producing medium in the closed container 12 is imported to second way of turning round the cold-producing medium ingress pipe (coolant channel) 92 of compression unit 34, be connected to towards the refrigerant discharge leader 96 of the inlet of gas cooler 154 by the magnetic valve 159 that constitutes the first stream control device.
On the other hand, another defrosting pipe 168 that is communicated with the pipe arrangement between refrigerant discharge leader 96 and expansion valve 156 and the evaporimeter 157 is set, another magnetic valve 169 that constitutes the first stream control device is set with getting involved at this defrosting pipe 168.In addition, the cold-producing medium ingress pipe 92 in the downstream of the branch point 170 of defrosting pipe 158 is provided as the capillary 160 of second decompressor and is connected to the magnetic valve 163 of the second stream control device of this capillary 160 side by side.
The switching of the valve of magnetic valve 159,169 and magnetic valve 163 is controlled by control device 164.Magnetic valve 163 is open when common heating moves by control device 164, closes when Defrost operation.Like this, supply to during Defrost operation second the revolution compression unit 34 refrigerant gas reduce pressure by the capillary 160 (decompressor) of being located at cold-producing medium ingress pipe 92 (coolant channel) after, supply to second the revolution compression unit 34.Like this, produce pressure differential in the suction side of the second revolution compression unit 34 with the discharge side like that as described later, so, can prevent that blade from takeofing, the irregular operation situation in the time of can avoiding Defrost operation improves reliability.
Constitute explanation action by above below.Control device 164 cuts out magnetic valve 159,169 when the heating operation, magnetic valve 163 is opened as described above.When the stator coil 28 of electrodynamic element 14 being switched on by terminal 20 and not shown distribution, electrodynamic element 14 startings, rotor 24 revolutions.Make the up-down roller 46,48 that is coupled to the eccentric part up and down 42,44 that is wholely set with gyroaxis 16 in upper and lower air cylinders 38,40, carry out the off-centre revolution by this revolution.
Like this, via cold-producing medium ingress pipe 94 and the suction passage 60 that is formed at lower support member 56, to be drawn into the refrigerant gas of low pressure (first order suction pressure LP:4MPa) of the low-pressure chamber side of lower cylinder 40 by the action compresses of cylinder 48 and blade from inlet hole 162, become intermediate pressure (MP1:8MPa), be discharged in the closed container 12 from middle discharge pipe 121 through not shown access from the not shown tap of the hyperbaric chamber side of lower cylinder 40, the discharge anechoic room 64 that is formed at lower support member 56.Make thus and become intermediate pressure (MP1) in the closed container 12.
The refrigerant gas of the intermediate pressure in the closed container 12 is from the cold-producing medium ingress pipe 92 of sleeve pipe 144 come out (middle discharge pressure is above-mentioned MP1), the magnetic valve 163 of the capillary 160 by being connected to this cold-producing medium ingress pipe 92 side by side is drawn into the low-pressure chamber side (second level suction pressure) of upper cylinder 38 from inlet hole 161 via the suction passage 58 that is formed at upper support member 54.The refrigerant gas of the intermediate pressure that sucks carries out second level compression by the action of last cylinder 46 and not shown blade, become the refrigerant gas (second level discharge pressure HP:12MPa) of HTHP, flow into gas cooler 154 by not shown tap via the discharge anechoic room 62 that is formed at upper support member 54, refrigerant discharge leader 96 from the hyperbaric chamber side.At this moment, refrigerant temperature is raised to substantially+100 ℃, and the refrigerant gas of this HTHP heats the water in the hot water storage tank from gas cooler 154 heat radiations, produces substantially+90 ℃ hot water.
On the other hand, cold-producing medium is come out from gas cooler 154 from cooling off in gas cooler 154.After expansion valve 156 decompressions, flow into evaporimeter 157 evaporations (this moment is from heat absorption on every side), be drawn in the first revolution compression unit 32 from cold-producing medium ingress pipe 94 through reservoir, and carry out this circulation repeatedly.
Particularly under the environment of low outside air temperature, such heating operation makes in evaporimeter 157 frostings.For this reason, control device 164 is opened magnetic valve 159,169 termly or according to indication operation arbitrarily, closes magnetic valve 163, in addition, makes expansion valve 156 standard-sized sheets, carries out the Defrost operation of evaporimeter 157.By opening magnetic valve 159 and 169, make the downstream that flows to expansion valve 156 from the closed container 12 interior refrigerant gas of the first revolution compression unit, 32 discharges through cold-producing medium ingress pipe 92, defrosting pipe 158, refrigerant discharge leader 96, defrosting pipes 168, or mobile through gas cooler 154 and expansion valve 156 (full-gear), flowing by both party all can be fed directly to evaporimeter 157 with not reducing pressure.
In addition, from the refrigerant gas process refrigerant discharge leader 96 of the second revolution compression unit, 34 discharges, the downstream that defrosting pipe 168 flows to expansion valve 156, be not fed directly to evaporimeter 157 with not reducing pressure.By the inflow heating fumigators 157 of this high temperature refrigerant gas, the frosting fusing is removed.
By open magnetic valve 159 and magnetic valve 169, the discharge side and the suction side of the second revolution compression unit 34 are communicated with by refrigerant discharge leader 96, defrosting pipe 158, cold-producing medium ingress pipe 92, so, become uniform pressure according to former state, but in the present invention, magnetic valve 163 cuts out during Defrost operation, so, between the suction side (cold-producing medium ingress pipe 92 sides) of the second revolution compression unit 34 and discharge side (refrigerant discharge leader 96 sides), capillary 160 is set.
Like this, supply to the second revolution compression unit 34 by being discharged in the closed container 12 after 32 compressions of the first revolution compression unit and supplying to second refrigerant gas that turns round compression unit 34 by this capillary 160 by cold-producing medium ingress pipe 92.That is, by capillary 160 decompressions, so, produce pressure differential in the suction side of the second revolution compression unit 34 with discharging side, prevent takeofing of blade thus, the unsettled operation conditions when avoiding Defrost operation can improve reliability.
This Defrost operation is for example according to end such as the regulation of evaporimeter 157 defrosting end temp and times.When the defrosting of control device 164 finishes, close each magnetic valve 159,169, open magnetic valve 163 and return to common heating operation.
In an embodiment, multi-stage compression formula rotary compressor 10 is used for the refrigerant loop of hot water supply apparatus 153, but is not limited thereto, it is also effective to the present invention to be used for indoor heating installation etc.In addition, in an embodiment, adopted the multi-stage compression formula rotary compressor of intermediate pressure type, but be not limited thereto, also effective when the cold-producing medium of discharging from the first revolution compression unit 32 supplies to the second revolution compression unit 34 in closed container 12 but by cold-producing medium ingress pipe 92.
As described above in detail, according to a first aspect of the present invention, rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container revolution compression unit compresses the CO2 cold-producing medium; Wherein, comprise the cylinder that constitutes the revolution compression unit, has the oscillating-piston that engages with the eccentric part of the gyroaxis that is formed at electrodynamic element and in cylinder, carry out the eccentric cylinder portion that moves, be formed at this oscillating-piston and will be divided into the blade part of low-pressure chamber side and hyperbaric chamber side in the cylinder towards radially giving prominence to from cylinder portion, and be located at cylinder and can be free to slide and swingingly keep the maintaining part of the blade part of oscillating-piston, so, corresponding with the off-centre revolution of the eccentric part of gyroaxis, oscillating-piston is the center swing with the maintaining part and slides that its blade part will be divided into low-pressure chamber side and hyperbaric chamber side often in the cylinder.
Like this, there is no need as the past, to be provided with towards the cylinder side blade is applied the spring of power and back pressure chamber and applies the structure of back pressure at this back pressure chamber, can realize the simplification of structure of rotary compressor and the reduction of production cost.
According to a second aspect of the present invention, rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units will be by the CO of the first revolution compression unit compression 2Refrigerant gas is discharged in the closed container, in addition, is compressed the refrigerant gas of the intermediate pressure of this discharge by the second revolution compression unit; Wherein, comprise the cylinder that constitutes the second revolution compression unit, has the oscillating-piston that engages with the eccentric part of the gyroaxis that is formed at electrodynamic element and in cylinder, carry out the eccentric cylinder portion that moves, be formed at this oscillating-piston and will be divided into the blade part of low-pressure chamber side and hyperbaric chamber side in the cylinder towards radially giving prominence to from cylinder portion, and be located at cylinder and can be free to slide and swingingly keep the maintaining part of the blade part of oscillating-piston, so, corresponding with the off-centre revolution of the eccentric part of gyroaxis, oscillating-piston is the center swing with the maintaining part and slides that its blade part is divided into low-pressure chamber side and hyperbaric chamber side in the cylinder with the second revolution compression unit often.
Like this, do not need as the past blade to be applied the spring and the back pressure chamber of power and this back pressure chamber is applied the structure of back pressure towards the cylinder side.Particularly become in the closed container as the present invention in the so-called multi-stage compression formula rotary compressor of intermediate pressure, apply the complex structureization of back pressure, but by using oscillating-piston, simplified construction and production cost significantly.
According to a third aspect of the present invention, on the basis of first or second invention, constitute maintaining part by gathering sill and sleeve, the blade part that this gathering sill is formed at cylinder and oscillating-piston enters wherein with can move freely, this sleeve can be located at this gathering sill freely to rotate and can keep blade part with being free to slide, so, can realize the swing of oscillating-piston and the tranquilization of sliding action. like this, can increase substantially the Performance And Reliability of rotary compressor.
As described above in detail according to the present invention, multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, to be attracted to the above-mentioned second revolution compression unit by the first revolution compression unit compression and the refrigerant gas of discharging, and compress the back and discharge; Wherein, be provided with the cold-producing medium suction side and cold-producing medium access of discharging side and the valve gear that opens and closes this access that are communicated with the first revolution compression unit, the pressure differential that this valve gear is discharged side at the first revolution cold-producing medium suction side of compression unit and cold-producing medium reaches the set upper limit value when above, the open communication road, so, can will be suppressed to below the set upper limit value as the cold-producing medium suction side of the first revolution compression unit of the level differential pressure of the first order pressure differential with cold-producing medium discharge side.Like this, the level differential pressure that can in advance avoid the first order is excessive and cause being located at the problems such as dump valve breakage of the first revolution compression unit, can improve the durability and the reliability of rotary compressor.
According to a fifth aspect of the present invention, has the cylinder that constitutes the first revolution compression unit, the opening surface of inaccessible this cylinder also has the supporting member of bearing of the gyroaxis of electrodynamic element, be formed in the suction passage in this supporting member and discharge anechoic room, in supporting member, form access, suction passage and discharge anechoic room are communicated with, simultaneously, valve gear is located in the supporting member, so access and valve gear are intensive in the cylinder of the first revolution compression unit, can realize miniaturization, simultaneously, because assembled valve device in cylinder in advance is so assembling operation also improves.
As described above in detail, according to the present invention, the first and second revolution compression units that in closed container, have electrodynamic element and drive by this electrodynamic element, to be attracted to the second revolution compression unit, the discharge of compression back by first refrigerant gas that turns round the intermediate pressure of compression unit compression; Wherein, be provided with connection and discharge the access of side and the valve gear that this access is opened and closed by the cold-producing medium that passes through the path and the second revolution compression unit of the refrigerant gas of the intermediate pressure of the first revolution compression unit compression, the pressure differential that this valve gear is discharged the refrigerant gas of side at the cold-producing medium of the refrigerant gas of intermediate pressure and the second revolution compression unit reaches the occasion more than the set upper limit value, the open communication road, so, can be that second level differential pressure suppresses lowlyer than set upper limit value with the pressure differential of discharge pressure and the suction pressure of the second revolution compression unit.
Like this, can avoid the faults such as breakage of the dump valve of the second revolution compression unit to take place in advance.
According to a seventh aspect of the present invention, on the basis of foregoing, have cylinder that constitutes the second revolution compression unit and the discharge anechoic room of discharging refrigerant compressed gas in this cylinder, to be discharged in the closed container by first refrigerant gas that turns round the intermediate pressure of compression unit compression, the second revolution compression unit attracts the refrigerant gas of the intermediate pressure in this closed container, simultaneously, access is formed on and surrounds in the wall of discharging anechoic room, be communicated with in the closed container and the discharge anechoic room, valve gear is located in the above-mentioned wall, so, can in the lid of the second revolution compression unit, intensive connection turn round the valve gear that the cold-producing medium of compression unit is discharged the access of side and opened and closed access by the path and second of passing through of the refrigerant gas of the intermediate pressure of the first revolution compression unit compression.
Like this, can realize the simplification of constructing and the miniaturization of overall dimensions.
As described above in detail according to the present invention, multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, to be discharged in the closed container by the first revolution compression unit refrigerant compressed gas, in addition, compress the gas of the intermediate pressure of this discharge by the second revolution compression unit; Wherein, has the cylinder that is used to constitute the second revolution compression unit, join to be incorporated in the gyroaxis eccentric part that is formed at electrodynamic element and carry out eccentric rotating cylinder in the cylinder, be contacted with this cylinder ground and will be divided into the blade of low-pressure chamber side and hyperbaric chamber side in the cylinder, be used for towards the cylinder side this blade being applied often the back pressure chamber of power, the cold-producing medium that is communicated with the second revolution compression unit is discharged the access of side and back pressure chamber, be used to adjust the pressure-regulating valve that is added to the pressure of back pressure chamber by this access, it is low to make the cold-producing medium of the pressure ratio second revolution compression unit of back pressure chamber discharge the pressure of side, and, remain the setting higher than the pressure in the closed container, thereby prevent that so-called blade from takeofing, and prevent to apply above the back pressure that needs, the power optimization that blade is applied cylinder at blade.
Like this, can alleviate the burden of the slipper that is applied to blade front end and cylinder periphery, improve the durability of the cylinder of blade, avoid the breakage of blade and cylinder in advance.
According to a tenth aspect of the present invention, on the basis of foregoing, also be provided with inaccessible cylinder opening surface and have electric element gyroaxis bearing supporting member and be formed in anechoic room in this supporting member, in supporting member, form access, be communicated with and discharge anechoic room and back pressure chamber, and, pressure-regulating valve is arranged in the supporting member, so, can effectively utilize the limited space in the closed container, and not make complex structureization can adjust the interior pressure of back pressure chamber of blade.In addition, owing in advance access and pressure-regulating valve are set in supporting member, so assembling operation is also good.
As described in detail above like that according to the present invention, multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units, these first and second revolutions compression units are by first and second cylinders and engage with first and second eccentric parts of the gyroaxis that is formed at above-mentioned electrodynamic element and carry out rotating first and second cylinders of off-centre constitute in cylinder, simultaneously, the refrigerant gas of being discharged by the above-mentioned first revolution compression unit compression back attracted to the second revolution compression unit, and discharge the compression back; When making this multi-stage compression formula rotary compressor, do not change thickness (highly) size of first cylinder, by changing the internal diameter of this cylinder, can set the eliminating volumetric ratio of the first and second revolution compression units, so, do not change all parts such as eccentric part of the first revolution cylinder material of compression unit and cylinder, gyroaxis, only change cylinder or only change cylinder and eccentric part etc. but for example do one's utmost to be suppressed to, thereby can reduce cost.In addition, can prevent the expansion of the overall dimensions of compressor, so, also can make compact in size.For example in the occasion below 75% more than 40% of the eliminating volume settings to the first of the second revolution compression unit being turned round the eliminating volume of compression unit as second invention, the eliminating volumetric ratios of the first and second revolution compression units are best.
As described above in detail, according to the present invention, refrigerant loop by multi-stage compression formula rotary compressor, gas cooler, first decompressor, and evaporimeter constitute; This multi-stage compression formula rotary compressor has electrodynamic element and driven by this electrodynamic element in closed container the first and second revolution compression units turn round the compression unit compression by the cold-producing medium after the first revolution compression unit compression by second; This gas cooler flows into wherein the cold-producing medium of discharging from the second revolution compression unit of this multi-stage compression formula rotary compressor; This first decompressor is connected to the outlet side of this gas cooler, and this evaporimeter is connected to the outlet side of this first decompressor; The cold-producing medium that comes out from this evaporimeter is compressed by the first revolution compression unit; Wherein, have and do not supply with from the defrost circuit of the cold-producing medium of the first and second revolution compression units discharges to evaporimeter with reducing pressure, control the first stream control device of the cold-producing medium circulation of this defrost circuit, be located at and be used for to supply to second decompressor of the coolant channel of the second revolution compression unit from the cold-producing medium of the first revolution compression unit discharge, make cold-producing medium flow to this second decompressor or make cold-producing medium walk around the second stream control device that this second decompressor is controlled with flowing through, when making cold-producing medium flow to defrost circuit by the first stream control device, this second stream control device makes cold-producing medium flow to second decompressor, so, during the evaporator defrost operation, the discharging refrigerant of the first revolution compression unit and the second revolution compression unit does not supply to evaporimeter with not reducing pressure, can avoid the pressure of the second revolution compression unit to reverse phenomenon thus.
Particularly according to the present invention, when carrying out this defrosting, the cold-producing medium that supplies to the second revolution compression unit supplies to the second revolution compression unit by the decompressor of being located at coolant channel, so, the pressure differential of formation regulation between suction in the second revolution compression unit and the discharge.
Like this, the operation of the second revolution compression unit is also stable, and reliability improves.Particularly as a fourteenth aspect of the present invention, with CO 2In the refrigerant loop of gas as the cold-producing medium use, particularly can obtain obvious effects.

Claims (3)

1. multi-stage compression formula rotary compressor, the first and second revolution compression units that in closed container, have electrodynamic element and drive by this electrodynamic element, to be attracted to the above-mentioned second revolution compression unit by above-mentioned first revolution compression unit compression and the refrigerant gas of discharging, and compress the back and discharge; It is characterized in that:
Be provided with the cold-producing medium suction side and cold-producing medium access of discharging side and the valve gear that opens and closes this access that are communicated with the above-mentioned first revolution compression unit,
The pressure differential that this valve gear is discharged side at the above-mentioned first revolution cold-producing medium suction side of compression unit and cold-producing medium reaches the set upper limit value when above, open above-mentioned access.
2. multi-stage compression formula rotary compressor according to claim 1 is characterized in that: have:
Constitute above-mentioned first the revolution compression unit cylinder,
The opening surface of inaccessible this cylinder and have above-mentioned electrodynamic element gyroaxis bearing supporting member,
Be formed in the suction passage in this supporting member and discharge anechoic room,
Form above-mentioned access in above-mentioned supporting member, above-mentioned suction passage and discharge anechoic room are communicated with, simultaneously, above-mentioned valve gear is located in the above-mentioned supporting member.
3. multi-stage compression formula rotary compressor, the first and second revolution compression units that in closed container, have electrodynamic element and drive by this electrodynamic element, to be attracted to the above-mentioned second revolution compression unit, the discharge of compression back by above-mentioned first refrigerant gas that turns round the intermediate pressure of compression unit compression; It is characterized in that:
Be provided with connection and discharge the access of side and the valve gear that this access is opened and closed by the cold-producing medium that passes through path and the above-mentioned second revolution compression unit of the refrigerant gas of the intermediate pressure of the above-mentioned first revolution compression unit compression,
The pressure differential that this valve gear is discharged the refrigerant gas of side at the cold-producing medium of the refrigerant gas of above-mentioned intermediate pressure and the above-mentioned second revolution compression unit reaches the occasion more than the set upper limit value, open above-mentioned access,
Constitute above-mentioned second the revolution compression unit cylinder and
The discharge anechoic room of discharge refrigerant compressed gas in this cylinder,
To be discharged in the above-mentioned closed container by above-mentioned first refrigerant gas that turns round the intermediate pressure of compression unit compression, the above-mentioned second revolution compression unit attracts the refrigerant gas of the intermediate pressure in this closed container, simultaneously,
Above-mentioned access is formed in the wall that surrounds above-mentioned discharge anechoic room, is communicated with in the above-mentioned closed container and the discharge anechoic room, and above-mentioned valve gear is located in the above-mentioned wall.
CN 200610006023 2001-11-30 2002-08-28 Multistage compression type rotary compressor Expired - Fee Related CN1807895B (en)

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
JP2001366209A JP3895976B2 (en) 2001-11-30 2001-11-30 Multistage rotary compressor
JP366209/2001 2001-11-30
JP2001366210A JP2003166489A (en) 2001-11-30 2001-11-30 Manufacturing method for multi-stage compression type rotary compressor
JP366210/2001 2001-11-30
JP374296/2001 2001-12-07
JP2001374296A JP3762693B2 (en) 2001-12-07 2001-12-07 Multi-stage rotary compressor
JP015350/2002 2002-01-24
JP2002015350A JP2003214366A (en) 2002-01-24 2002-01-24 Rotary compressor
JP021338/2002 2002-01-30
JP2002021338A JP3762708B2 (en) 2002-01-30 2002-01-30 Multistage rotary compressor
JP2002028857A JP2003227665A (en) 2002-02-06 2002-02-06 Defroster of refrigerant circuit
JP028857/2002 2002-02-06

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CN02142300A Division CN1423055A (en) 2001-11-30 2002-08-28 Revolving compressor, its manufacturing method and defrosting device using said compressor

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CN1807895A CN1807895A (en) 2006-07-26
CN1807895B true CN1807895B (en) 2010-05-12

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CN 200610006025 Expired - Fee Related CN1807896B (en) 2001-11-30 2002-08-28 Multi-stage compression type rotary compressor
CNB2006100060243A Expired - Fee Related CN100366993C (en) 2001-11-30 2002-08-28 Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit

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CN102953997B (en) * 2012-10-26 2015-04-22 珠海格力电器股份有限公司 Rotary compressor with compression pump body separated from motor
CN104235388B (en) * 2014-09-30 2016-05-25 贾培育 A kind of large capacity defrosting valve
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JP3895976B2 (en) 2007-03-22
CN1807896B (en) 2011-05-04
JP2003166488A (en) 2003-06-13
CN100366993C (en) 2008-02-06
CN1821686A (en) 2006-08-23
CN1807895A (en) 2006-07-26
CN1807896A (en) 2006-07-26

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